CN112443642A

CN112443642A - Torque vector distribution device

Info

Publication number: CN112443642A
Application number: CN202010918326.8A
Authority: CN
Inventors: 矶野宏
Original assignee: Toyota Motor Corp
Current assignee: Toyota Motor Corp
Priority date: 2019-09-03
Filing date: 2020-09-03
Publication date: 2021-03-05
Also published as: US20210062903A1; JP2021038785A; EP3789634A1; US11181177B2

Abstract

The torque vector distribution device of the present invention includes: a differential mechanism capable of realizing differential rotation of a first drive shaft and a second drive shaft to which power torque of a power source is transmitted; an actuator for applying a control torque to the differential mechanism to differentially rotate the drive shafts; and an inversion mechanism that rotates the drive shafts in directions opposite to each other, wherein the inversion mechanism is configured by a first control planetary gear mechanism that transmits the control torque to the first drive shaft via a first differential reaction element of the differential mechanism and a second control planetary gear mechanism that transmits the control torque to the second drive shaft via a second differential reaction element of the differential mechanism, and the gear ratio of the first gear train in the first control planetary gear mechanism and the gear ratio of the second gear train in the second control planetary gear mechanism are made different from each other.

Description

Torque vector distribution device

Technical Field

The present invention relates to a torque vector distribution device that actively controls the distribution (distribution ratio) of torque transmitted to right and left drive shafts.

Background

Patent document 1 describes an example of a drive gear device mounted on a vehicle. The drive gear device described in patent document 1 is a so-called torque vector distribution device, and includes: a differential mechanism that distributes and transmits an output torque of a drive power source to left and right drive wheels; and a control (differential) motor for controlling a distribution ratio of torque transmitted from the differential mechanism to the left and right drive wheels. The differential mechanism is composed of two sets of single pinion type planetary gear mechanisms. In the example shown in fig. 1 of patent document 1, the sun gears of the two planetary gear mechanisms serve as input elements, the carriers serve as output elements, and the ring gears serve as reaction force elements. Specifically, the sun gears of the two planetary gear mechanisms are coupled to each other by a coupling shaft. An input gear to which torque is transmitted from a driving force source is provided at a central portion of the coupling shaft. Left and right drive wheels are connected to the respective wheel carriers via drive shafts (output shafts). The left and right ring gears are coupled to each other via a reversing mechanism (reverse rotation member). A control motor is connected to one of the ring gears so as to be able to transmit torque. The reversing mechanism is constituted by a first gear member and a second gear member. The first gear member has a first pinion gear that meshes with an external gear formed on an outer peripheral portion of one of the ring gears, a shaft member, and a second pinion gear. A first pinion and a second pinion are fitted to both ends of the shaft member, respectively. Similarly, the second gear member has a first pinion gear, a shaft member, and a second pinion gear that mesh with an external gear formed on an outer peripheral portion of the other ring gear. A first pinion and a second pinion are fitted to both ends of the shaft member, respectively. And, the second pinion of the first gear member meshes with the second pinion of the second gear member. Therefore, the reversing mechanism reverses the rotational direction of the torque of the control motor input to one of the ring gears between the left and right ring gears to transmit the torque to the other ring gear.

In the example shown in "fig. 19" of patent document 1, the ring gears of the two planetary gear mechanisms serve as input elements, the carriers serve as output elements, and the sun gears serve as reaction force elements. Specifically, the ring gears of the two planetary gear mechanisms are coupled to each other by a coupling member so as to be able to transmit torque. The coupling member has: a first pinion gear that meshes with an external gear formed on an outer peripheral portion of one of the ring gears; a second pinion gear that meshes with an external gear formed on an outer peripheral portion of the other ring gear; and a shaft member. A first pinion and a second pinion are fitted to both ends of the shaft member, respectively. Further, the drive gear to which the torque from the drive force source is transmitted is meshed with the external gear of one of the ring gears. Left and right drive wheels are connected to the respective wheel carriers via drive shafts (output shafts). Further, instead of the coupling shaft as described above, the sun gears are coupled to each other via a counter-rotation motor unit. The reverse rotation motor unit is composed of a motor and a gear mechanism. One end of the rotor shaft of the motor forms a first output shaft in the counter-rotating motor unit. A pinion gear is attached to the other end of the rotor shaft, and the pinion gear meshes with a first counter gear (counter gear) of the gear mechanism. The first counter gear is attached to one end of the counter gear shaft. The second counter gear is attached to the other end of the counter gear shaft. The second counter gear meshes with an internal gear of a rotary member formed with a second output shaft in the counter-rotating motor unit. The first output shaft and the second output shaft are coaxially arranged. The first output shaft is connected to one of the sun gears. The second output shaft is connected to the other sun gear. Therefore, the reverse rotation motor unit reverses the rotation direction of the torque of the motor input to one sun gear between the left and right sun gears to transmit the torque to the other sun gear. That is, the reverse rotation motor unit functions as the control motor and the reversing mechanism as described above.

Documents of the prior art

Patent document

Patent document 1: japanese patent No. 6122119

Problems to be solved by the invention

The drive gear device described in patent document 1 is assumed to be mounted on a vehicle as a torque vector distribution device. In order to facilitate mounting on a vehicle, it is desirable to reduce the external shape of the device as much as possible. In the example shown in "fig. 1" of patent document 1, the reversing mechanism is disposed on the outer peripheral side of each ring gear in the left and right planetary gear mechanisms. The control (differential) motor is also disposed on the outer peripheral side of each ring gear. Therefore, the outer shape increases in the radial direction of the device. In contrast, for example, if a speed reduction mechanism having a larger speed reduction ratio is provided between the control motor and the ring gear, the control motor can be downsized. Alternatively, a larger torque for control or differential can be obtained. However, since the speed reduction mechanism is newly provided, the external shape of the apparatus may be increased as a result.

On the other hand, in the example shown in "fig. 19" of patent document 1, a counter-rotation motor unit serving as both a reversing mechanism and a control motor is disposed between the sun gears in the left and right planetary gear mechanisms. Therefore, there is a possibility that the size of the apparatus in the radial direction can be suppressed as compared with the example shown in "fig. 1" of patent document 1. However, it is not easy to arrange the counter-rotating motor unit between the sun gears while suppressing the increase in size in the radial direction. The counter-rotating motor unit has a two-shaft structure in which the first output shaft and the second output shaft are arranged in parallel with the counter gear shaft, and the structure becomes complicated. Further, if a reduction mechanism is provided to reduce the size of the motor or to obtain a larger torque, the structure becomes more complicated. As a result, for example, it is difficult to house the counter-rotation motor unit within the range of the outer diameter of the planetary gear mechanism, and as a result, the external shape of the device may increase.

Disclosure of Invention

The present invention has been made in view of the above-described problems, and an object thereof is to provide a torque vector distribution device that is compact in size and easy to mount on a vehicle.

Means for solving the problems

In order to achieve the above object, the present invention provides a torque vector distribution device including: an input member to which power torque is input from a power source; a first drive shaft and a second drive shaft which are coaxially arranged to face each other in the left-right direction and are rotatable relative to each other; a differential mechanism that, between the input member and the first and second drive shafts, distributes and transmits the motive torque input to the input member to the first and second drive shafts, and enables differential rotation of the first and second drive shafts; an actuator that imparts a control torque to the differential mechanism to differentially rotate the first drive shaft and the second drive shaft; and a reverse rotation mechanism that rotates the first drive shaft and the second drive shaft in directions opposite to each other when the first drive shaft and the second drive shaft are differentially rotated, wherein the differential mechanism is composed of a first power planetary gear mechanism and a second power planetary gear mechanism that are coaxially disposed so as to face each other in the left-right direction, and the first power planetary gear mechanism includes: a power input element to which the power torque is transmitted from the input member; a first power output element that outputs the power torque to the first drive shaft; and a first differential reaction force element to which the control torque is transmitted as a reaction force against the power torque transmitted from the power input element to the first power output element, the second power planetary gear mechanism having: the power input element; a second power output element that outputs the motive torque to the second drive shaft; and a second differential reaction element to which the control torque is transmitted as a reaction force against the power torque transmitted from the power input element to the second power output element, the reaction mechanism being constituted by a first control planetary gear mechanism and a second control planetary gear mechanism arranged coaxially with the first drive shaft and the second drive shaft, respectively, the first control planetary gear mechanism transmitting the control torque to the first drive shaft via the first differential reaction element, the second control planetary gear mechanism transmitting the control torque to the second drive shaft via the second differential reaction element, the first control planetary gear mechanism having: a control input element to which the control torque is input from the actuator; a first control output element that outputs the control torque to the first drive shaft; a first planetary gear to which the control torque is transmitted from the control input element; and a first gear meshed with the first planetary gear to form the control input element or the first control output element, the second control planetary gear mechanism having: the control input element; a second control output element that outputs the control torque to the second drive shaft; a second planetary gear arranged coaxially with the first planetary gear, the control torque being transmitted from the control input element; and a second gear engaged with the second planetary gear to form the control input element or the second control output element, a gear ratio of a first gear train including the first planetary gear and the first gear and a gear ratio of a second gear train including the second planetary gear and the second gear being different from each other.

Further, the invention is characterized in that, as for the reversing mechanism, a first reduction gear ratio representing a proportion of the rotation speed of the first control output element relative to the rotation speed of the control input element and a second reduction gear ratio representing a proportion of the rotation speed of the second control output element relative to the rotation speed of the control input element are both larger than "1", and the reversing mechanism forms a reduction gear mechanism that amplifies and transmits the control torque to the first control output element and the second control output element.

In the differential mechanism, the input member is coupled to the power input element, the first power output element is coupled to the first drive shaft, the second power output element is coupled to the second drive shaft, the actuator is coupled to the control input element, the first gear forms the first control output element, the second gear forms the second control output element, and the reverse mechanism amplifies the control torque input to the control input element and transmits the amplified control torque to the first drive shaft and the second drive shaft.

Further, the present invention is characterized in that the reversing mechanism is rotated together with the power input element and the first and second power output elements when the first drive shaft and the second drive shaft are rotated in the same direction at the same speed.

The present invention is characterized by comprising: a third planetary gear disposed coaxially with the first planetary gear and the second planetary gear; and a carrier that holds the planetary gears so as to be rotatable and revolvable, wherein the first planetary gear, the second planetary gear, and the third planetary gear rotate integrally in a rotation direction, and the third planetary gear is transmitted with the power torque from the power input element.

The present invention is characterized by comprising: third and fourth planet gears arranged coaxially with the first and second planet gears, respectively; and a carrier that holds the planetary gears to be rotatable and revolvable, respectively, the first planetary gear and the third planetary gear being rotatable integrally in a rotation direction, the second planetary gear and the fourth planetary gear being rotatable integrally in the rotation direction, the first planetary gear and the third planetary gear and the second planetary gear and the fourth planetary gear being rotatable relative to each other, the third planetary gear and the fourth planetary gear each being transmitted with the power torque from the power input element.

In addition, the present invention is characterized in that the differential mechanism includes: the first, second, and third planet gears; a first sun gear, a second sun gear, and a third sun gear arranged on a same axis, the first sun gear being in mesh with the first planetary gear, the second sun gear being in mesh with the second planetary gear, the third sun gear being in mesh with the third planetary gear; and the carrier, the first sun gear, the second sun gear, and the third sun gear being rotatable relative to each other, the third sun gear serving as the power input element, the first sun gear serving as the first power output element, the carrier serving as the first differential reaction element, and constituting the first power planetary gear mechanism, the third sun gear serving as the power input element, the second sun gear serving as the second power output element, the carrier serving as the second differential reaction element, and constituting the second power planetary gear mechanism, the inversion mechanism including: the first, second, and third planet gears; the first sun gear, the second sun gear, and the third sun gear; and the carrier which becomes the control input element, the first sun gear which becomes the first control output element as the first gear, thereby constituting the first control planetary gear mechanism, the carrier which becomes the control input element, the second sun gear which becomes the second control output element as the second gear, thereby constituting the second control planetary gear mechanism, the number of teeth of the first sun gear and the number of teeth of the second sun gear are both equal to the number of teeth of the third sun gear, the number of teeth of the first planetary gear is more than the number of teeth of the third planetary gear, and the number of teeth of the second planetary gear is less than the number of teeth of the third planetary gear.

In addition, the present invention is characterized in that the differential mechanism includes: the first, second, and third planet gears; a first sun gear, a second sun gear, and a third sun gear arranged on a same axis, the first sun gear being in mesh with the first planetary gear, the second sun gear being in mesh with the second planetary gear, the third sun gear being in mesh with the third planetary gear; the wheel carrier; and an internal gear ring gear that meshes with the third planetary gear, the first sun gear, the second sun gear, and the third sun gear being rotatable relative to each other, the third sun gear serving as the power input element, the first sun gear serving as the first power output element, and the ring gear serving as the first differential reaction element, thereby constituting the first power planetary gear mechanism, the third sun gear serving as the power input element, the second sun gear serving as the second power output element, and the ring gear serving as the second differential reaction element, thereby constituting the second power planetary gear mechanism, the inversion mechanism having: the first, second, and third planet gears; the first sun gear, the second sun gear, and the third sun gear; the wheel carrier; and the ring gear, the ring gear becomes the control input element, the first sun gear becomes the first control output element as the first gear, thereby constituting the first control planetary gear mechanism, the ring gear becomes the control input element, the second sun gear becomes the second control output element as the second gear, thereby constituting the second control planetary gear mechanism, the number of teeth of the first sun gear and the number of teeth of the second sun gear are both equal to the number of teeth of the third sun gear, the number of teeth of the first planetary gear is more than the number of teeth of the third planetary gear, and the number of teeth of the second planetary gear is less than the number of teeth of the third planetary gear.

In addition, the present invention is characterized in that the differential mechanism includes: the first, second, and third planet gears; a first ring gear of an internal gear, a second ring gear of an internal gear, and a third ring gear of an internal gear, which are coaxially arranged, the first ring gear being engaged with the first planetary gear, the second ring gear being engaged with the second planetary gear, the third ring gear being engaged with the third planetary gear; and the carrier, the first ring gear and the second ring gear being rotatable relative to each other, the third ring gear serving as the power input element, the first ring gear serving as the first power output element, the carrier serving as the first differential reaction element, and constituting the first power planetary gear mechanism, the third ring gear serving as the power input element, the second ring gear serving as the second power output element, and the carrier serving as the second differential reaction element, and constituting the second power planetary gear mechanism, the inversion mechanism having: the first, second, and third planet gears; the first gear ring, the second gear ring, and the third gear ring; and the carrier serving as the control input element, the first ring gear serving as the first gear and serving as the first control output element to constitute the first control planetary gear mechanism, the carrier serving as the control input element, and the second ring gear serving as the second gear and serving as the second control output element to constitute the second control planetary gear mechanism, the number of teeth of the first ring gear and the number of teeth of the second ring gear are both equal to the number of teeth of the third ring gear, the number of teeth of the first planetary gear is greater than the number of teeth of the third planetary gear, and the number of teeth of the second planetary gear is less than the number of teeth of the third planetary gear.

In addition, the present invention is characterized in that the differential mechanism includes: the first, second, and third planet gears; a first sun gear, a second sun gear, and a third sun gear arranged on a same axis, the first sun gear being in mesh with the first planetary gear, the second sun gear being in mesh with the second planetary gear, the third sun gear being in mesh with the third planetary gear; and the carrier, the first sun gear, the second sun gear, and the third sun gear being rotatable relative to each other, the third sun gear serving as the power input element, the first sun gear serving as the first power output element, the carrier serving as the first differential reaction element, and constituting the first power planetary gear mechanism, the third sun gear serving as the power input element, the second sun gear serving as the second power output element, the carrier serving as the second differential reaction element, and constituting the second power planetary gear mechanism, the inversion mechanism including: the first, second, and third planet gears; the first sun gear, the second sun gear, and the third sun gear; and the carrier serving as the control input element, the first sun gear serving as the first control output element, thereby constituting the first control planetary gear mechanism, the carrier serving as the control input element, the second sun gear serving as the second control output element, thereby constituting the second control planetary gear mechanism, the number of teeth of the first sun gear and the number of teeth of the second sun gear are both equal to the number of teeth of the third sun gear, the number of teeth of the first planetary gear is more than the number of teeth of the third planetary gear, and the number of teeth of the second planetary gear is smaller than the number of teeth of the third planetary gear, the torque vector distribution device further includes a reduction planetary gear mechanism, the reduction planetary gear mechanism amplifies and transmits the control torque between the actuator and the carrier to the carrier.

In addition, the present invention is characterized in that the differential mechanism includes: the first, second, and third planet gears; a first sun gear, a second sun gear, and a third sun gear arranged on a same axis, the first sun gear being in mesh with the first planetary gear, the second sun gear being in mesh with the second planetary gear, the third sun gear being in mesh with the third planetary gear; and the carrier, the first sun gear, the second sun gear, and the third sun gear being rotatable relative to each other, the third sun gear serving as the power input element, the first sun gear serving as the first power output element, the carrier serving as the first differential reaction element, and constituting the first power planetary gear mechanism, the third sun gear serving as the power input element, the second sun gear serving as the second power output element, the carrier serving as the second differential reaction element, and constituting the second power planetary gear mechanism, the inversion mechanism including: the first, second, and third planet gears; the first sun gear, the second sun gear, and the third sun gear; and the carrier, the torque vector distribution device further including a reduction planetary gear mechanism that amplifies the control torque between the actuator and the carrier and transmits the amplified control torque to the carrier, the reduction planetary gear mechanism being configured by a fourth sun gear, a ring gear, and the carrier, the fourth sun gear serving as the control input element, the first sun gear serving as the first gear and serving as the first control output element, thereby compositely configuring the first control planetary gear mechanism, the fourth sun gear serving as the control input element, the second sun gear serving as the second gear and serving as the second control output element, thereby compositely configuring the second control planetary gear mechanism, the number of teeth of the first sun gear and the number of teeth of the second sun gear being equal to each other, the number of teeth of the first planetary gear is greater than that of the third planetary gear, and the number of teeth of the second planetary gear is less than that of the third planetary gear.

In addition, the reduction planetary gear mechanism may include a fourth planetary gear that meshes with the fourth sun gear and the ring gear at the same time, the fourth planetary gear may be disposed coaxially with the first planetary gear, the second planetary gear, and the third planetary gear and may be rotatable relative to the first planetary gear, the second planetary gear, and the third planetary gear, and the carrier may hold the fourth planetary gear, the first planetary gear, the second planetary gear, and the third planetary gear together so as to be rotatable and revolvable, respectively.

In addition, the present invention is characterized in that the differential mechanism includes: the first, second, third, and fourth planet gears; a first ring gear of an internal gear, a second ring gear of an internal gear, a third ring gear of an internal gear, and a fourth ring gear of an internal gear, which are coaxially arranged, the first ring gear being engaged with the first planetary gear, the second ring gear being engaged with the second planetary gear, the third ring gear being engaged with the third planetary gear, the fourth ring gear being engaged with the fourth planetary gear; and the carrier, the third ring gear and the fourth ring gear integrally rotating, the first ring gear and the second ring gear and the third ring gear and the fourth ring gear being rotatable relative to each other, the third ring gear serving as the power input element, the first ring gear serving as the first power output element, the carrier serving as the first differential reaction element, thereby constituting the first power planetary gear mechanism, the fourth ring gear serving as the power input element, the second ring gear serving as the second power output element, the carrier serving as the second differential reaction element, thereby constituting the second power planetary gear mechanism, the inversion mechanism having: the first, second, third, and fourth planet gears; the first gear ring, the second gear ring, the third gear ring, and the fourth gear ring; and the carrier serving as the control input element, the first ring gear serving as the first control output element, thereby constituting the first control planetary gear mechanism, the carrier serving as the control input element, the second ring gear serving as the second control output element, thereby constituting the second control planetary gear mechanism, the number of teeth of the first planetary gear and the number of teeth of the second planetary gear are equal to the number of teeth of the third planetary gear and the number of teeth of the fourth planetary gear, the number of teeth of the first gear ring is equal to that of the second gear ring, the number of teeth of the third gear ring is less than that of the first gear ring and that of the second gear ring, and the number of teeth of the fourth ring gear is greater than the number of teeth of the first ring gear and the number of teeth of the second ring gear.

In the differential mechanism, the input member is coupled to the power input element, the first power output element is coupled to the first drive shaft, the second power output element is coupled to the second drive shaft, the first differential reaction force element and the second differential reaction force element are linked to the actuator via the reverse mechanism, for the reverse mechanism, the actuator is linked with the control input element, the first gear forms the control input element or the first control output element, the second gear forms the control input element or the second control output element, and the inversion mechanism amplifies and transmits the control torque input to the control input element to the first differential reaction element and the second differential reaction element.

In the present invention, the first control planetary gear mechanism and the second control planetary gear mechanism form a reduction gear mechanism that amplifies the control torque with respect to the reversing mechanism, and the reversing mechanism transmits the control torque amplified by the first control planetary gear mechanism to the first differential reaction element and transmits the control torque amplified by the second control planetary gear mechanism to the second differential reaction element.

The present invention is characterized by including a first output torque reduction mechanism and a second output torque reduction mechanism that are coaxially disposed so as to face each other in the left-right direction, the first output torque reduction mechanism amplifying torque transmitted to the first drive shaft, the second output torque reduction mechanism amplifying torque transmitted to the second drive shaft, the first power output element and the first drive shaft being coupled via the first output torque reduction mechanism, the second power output element and the second drive shaft being coupled via the second output torque reduction mechanism, and the reversing mechanism being disposed between the first output torque reduction mechanism and the second output torque reduction mechanism in the rotation axis direction.

Further, the present invention is characterized in that the reversing mechanism includes: a first planetary gear, a second planetary gear, a third planetary gear and a fourth planetary gear which are coaxially arranged; a first sun gear, a second sun gear, a third sun gear, and a fourth sun gear arranged on a same axis, the first sun gear being in mesh with the first planetary gear, the second sun gear being in mesh with the second planetary gear, the third sun gear being in mesh with the third planetary gear, the fourth sun gear being in mesh with the fourth planetary gear; and a carrier that holds the planetary gears to be rotatable and revolvable, respectively, wherein the first planetary gear and the third planetary gear are rotatable integrally in a rotation direction, the second planetary gear and the fourth planetary gear are rotatable integrally in a rotation direction, the first planetary gear and the third planetary gear and the second planetary gear and the fourth planetary gear are rotatable relative to each other, the third sun gear and the fourth sun gear are coupled, the first sun gear and the second sun gear and the third sun gear and the fourth sun gear are rotatable relative to each other, the first sun gear and the first differential reaction element are coupled, the second sun gear and the second differential reaction element are coupled, the carrier serves as the control input element, and the first sun gear serves as the first gear and serves as the first control output element, thereby constitute the first control planetary gear mechanism, the wheel carrier becomes the control input element, the second sun gear is regarded as the second gear and becomes the second control output element, thereby constitute the second control planetary gear mechanism, the number of teeth of first sun gear with the number of teeth of second sun gear with the number of teeth of third sun gear with the number of teeth of fourth sun gear all equals, the number of teeth of third planetary gear with the number of teeth of fourth planetary gear equals, the number of teeth of first planetary gear is more than the number of teeth of third planetary gear with the number of teeth of fourth planetary gear, and the number of teeth of second planetary gear is less than the number of teeth of third planetary gear with the number of teeth of fourth planetary gear.

Further, the present invention is characterized in that the reversing mechanism includes: a first planetary gear, a second planetary gear and a third planetary gear which are coaxially arranged; a first sun gear, a second sun gear, and a third sun gear arranged on a same axis, the first sun gear being in mesh with the first planetary gear, the second sun gear being in mesh with the second planetary gear, the third sun gear being in mesh with the third planetary gear; and a carrier that holds the planetary gears to be rotatable and revolvable, respectively, wherein the first planetary gear, the second planetary gear, and the third planetary gear are rotatable integrally in a rotation direction, the first sun gear, the second sun gear, and the third sun gear are rotatable relative to each other, the first sun gear is coupled to the first differential reaction element, the second sun gear is coupled to the second differential reaction element, the carrier serves as the control input element, the first sun gear serves as the first gear and serves as the first control output element, and the first control planetary gear mechanism is configured, the carrier serves as the control input element, and the second sun gear serves as the second gear and serves as the second control output element, and the second control planetary gear mechanism is configured, the number of teeth of first sun gear with the number of teeth of second sun gear with the number of teeth of third sun gear equals, the number of teeth of first planetary gear is less than the number of teeth of third planetary gear, and the number of teeth of second planetary gear is more than the number of teeth of third planetary gear.

Further, the present invention is characterized in that the reversing mechanism includes: a first planetary gear, a second planetary gear, a third planetary gear and a fourth planetary gear which are coaxially arranged; a first sun gear, a second sun gear, a third sun gear, and a fourth sun gear arranged on a same axis, the first sun gear being in mesh with the first planetary gear, the second sun gear being in mesh with the second planetary gear, the third sun gear being in mesh with the third planetary gear, the fourth sun gear being in mesh with the fourth planetary gear; a first ring gear of an internal gear, a second ring gear of an internal gear, a third ring gear of an internal gear, and a fourth ring gear of an internal gear, which are coaxially arranged, the first ring gear being engaged with the first planetary gear, the second ring gear being engaged with the second planetary gear, the third ring gear being engaged with the third planetary gear, the fourth ring gear being engaged with the fourth planetary gear; and a first carrier, a second carrier, and a third carrier that are coaxially arranged, the first carrier holding the first planetary gears to be rotatable and revolvable, the second carrier holding the second planetary gears to be rotatable and revolvable, the third carrier holding the third planetary gears and the fourth planetary gears to be rotatable and revolvable, the first planetary gears and the second planetary gears and the third planetary gears and the fourth planetary gears being rotatable relative to each other, the first sun gear and the third sun gear rotating integrally, the second sun gear and the fourth sun gear rotating integrally, the first sun gear and the third sun gear and the second sun gear and the fourth sun gear rotating relatively to each other, the first ring gear and the second ring gear and the third ring gear rotating integrally, the first carrier, the second carrier, and the third carrier are rotatable relative to each other, the first carrier is coupled to the first differential reaction force element, the second carrier is coupled to the second differential reaction force element, the first ring gear serves as the first gear and serves as the control input element, the first carrier serves as the first control output element, the first control planetary gear mechanism is configured, the second ring gear serves as the second gear and serves as the control input element, the second carrier serves as the second control output element, the second control planetary gear mechanism is configured, the number of teeth of the first planetary gear and the number of teeth of the second planetary gear are equal to the number of teeth of the third planetary gear and the number of teeth of the fourth planetary gear, and the number of teeth of the third sun gear and the number of teeth of the fourth sun gear are equal to each other, the number of teeth of first sun gear is less than the number of teeth of third sun gear with the number of teeth of fourth sun gear, and the number of teeth of second sun gear is more than the number of teeth of third sun gear with the number of teeth of fourth sun gear, the number of teeth of third ring gear with the number of teeth of fourth ring gear equals, the number of teeth of first ring gear is more than the number of teeth of third ring gear with the number of teeth of fourth ring gear, and the number of teeth of second ring gear is less than the number of teeth of third ring gear with the number of teeth of fourth ring gear.

Further, the present invention is characterized in that the reversing mechanism includes: a first planetary gear, a second planetary gear and a third planetary gear which are coaxially arranged; a first sun gear, a second sun gear, and a third sun gear arranged on a same axis, the first sun gear being in mesh with the first planetary gear, the second sun gear being in mesh with the second planetary gear, the third sun gear being in mesh with the third planetary gear; a first ring gear of an internal gear, a second ring gear of an internal gear, and a third ring gear of an internal gear, which are coaxially arranged, the first ring gear being engaged with the first planetary gear, the second ring gear being engaged with the second planetary gear, the third ring gear being engaged with the third planetary gear; and a first carrier, a second carrier, and a third carrier that are coaxially arranged, the first carrier holding the first planetary gear so as to be rotatable and revolvable, the second carrier holding the second planetary gear so as to be rotatable and revolvable, the third carrier holding the third planetary gear so as to be rotatable and revolvable, the first sun gear, the second sun gear, and the third sun gear both integrally rotate, the first ring gear, the second ring gear, and the third ring gear both integrally rotate, the first carrier, the second carrier, and the third carrier are rotatable relative to each other, the first carrier is coupled to the first differential reaction element, the second carrier is coupled to the second differential reaction element, and the first ring gear serves as the first gear and serves as the control input element, the first carrier becomes the first control output element to constitute the first control planetary gear mechanism, the second ring gear becomes the control input element as the second gear, the second carrier becomes the second control output element to constitute the second control planetary gear mechanism, the number of teeth of the first planetary gear, the number of teeth of the second planetary gear, and the number of teeth of the third planetary gear are all equal, the number of teeth of the first sun gear is smaller than the number of teeth of the third sun gear, and the number of teeth of the second sun gear is larger than the number of teeth of the third sun gear, the number of teeth of the first ring gear is larger than the number of teeth of the third ring gear, and the number of teeth of the second ring gear is smaller than the number of teeth of the third ring gear.

Further, the present invention is characterized in that the reversing mechanism includes: a first planetary gear, a second planetary gear and a third planetary gear which are coaxially arranged; a first sun gear, a second sun gear, and a third sun gear arranged on a same axis, the first sun gear being in mesh with the first planetary gear, the second sun gear being in mesh with the second planetary gear, the third sun gear being in mesh with the third planetary gear; an internal gear ring gear meshed with the second planetary gear; and a first carrier and a second carrier that are coaxially arranged, the first carrier holding the first planetary gear and the third planetary gear so as to be rotatable and revolvable, the second carrier holding the second planetary gear so as to be rotatable and revolvable, the first planetary gear and the third planetary gear integrally rotating in a rotation direction, the first planetary gear and the third planetary gear and the second planetary gear being rotatable relative to each other, the first sun gear and the second sun gear and the third sun gear being rotatable relative to each other, the first carrier and the second carrier being rotatable relative to each other, the first carrier and the second sun gear being coupled, the third sun gear and the ring gear being fixed so as to be non-rotatable, the first sun gear being coupled to the first differential reaction force element, the second carrier is coupled to the second differential reaction force element, the first carrier serves as the control input element, the first sun gear serves as the first gear and serves as the first control output element, thereby constituting the first control planetary gear mechanism, the second sun gear serving as the second gear serving as the control input element, the second carrier serving as the second control output element, thereby constituting the second control planetary gear mechanism, the gear ratio of the gear transmission path through which the control torque is transmitted to the first differential reaction element via the first carrier, the first planetary gears, and the first sun gear and the gear ratio of the gear transmission path through which the control torque is transmitted to the second differential reaction element via the second sun gear, the second planetary gears, and the second carrier are different from each other.

In the present invention, the input member has a hollow power torque output shaft for transmitting the power torque to the differential mechanism side, the actuator has a hollow control torque output shaft for transmitting the control torque to the reversing mechanism side, and the reversing mechanism is disposed in a hollow portion of the power torque output shaft and a hollow portion of the control torque output shaft.

In addition, the present invention is characterized in that the actuator has a first rotary shaft and a second rotary shaft which are coaxially arranged to face each other in the left-right direction, the first rotary shaft protrudes toward the first drive shaft and outputs the control torque, the second rotary shaft protrudes toward the second drive shaft and outputs the control torque, the first control planetary gear mechanism and the second control planetary gear mechanism are arranged separately in the left and right directions of the actuator in the rotation axis direction with respect to the reversing mechanism, the first control planetary gear mechanism has a first input shaft to which the control torque is input and a first output shaft which transmits the control torque to the first drive shaft side, the second control planetary gear mechanism has a second input shaft to which the control torque is input and a second output shaft which transmits the control torque to the second drive shaft side, the first rotating shaft is coupled to the first input shaft, the second rotating shaft is coupled to the second input shaft, the first output shaft is coupled to the first differential reaction element, the second output shaft is coupled to the second differential reaction element, and a gear ratio of a gear transmission path through which the control torque is transmitted to the first differential reaction element via the first rotating shaft, the first input shaft, and the first output shaft and a gear ratio of a gear transmission path through which the control torque is transmitted to the second differential reaction element via the second rotating shaft, the second input shaft, and the second output shaft are different from each other.

In the present invention, the actuator is an electric motor that outputs, as the control torque, a drive torque for driving the first differential reaction element and the second differential reaction element, or a brake mechanism that outputs, as the control torque, a brake torque for braking the first differential reaction element and the second differential reaction element.

In the present invention, the power source is at least one of an electric motor that outputs, as the motive torque, a driving torque for driving the first drive shaft and the second drive shaft, and a braking mechanism that outputs, as the motive torque, a braking torque for braking the first drive shaft and the second drive shaft.

Effects of the invention

The torque vector distribution device of the present invention distributes and transmits power torque input from a power source to right and left drive shafts (a first drive shaft and a second drive shaft) via a differential mechanism. At the same time, a difference in rotational speed between the first drive shaft and the second drive shaft is absorbed. That is, when a difference in rotational speed occurs between the first drive shaft and the second drive shaft, the first drive shaft and the second drive shaft are caused to rotate differentially. When the first drive shaft and the second drive shaft perform differential rotation, the first drive shaft and the second drive shaft relatively rotate in the opposite rotational directions to each other by the reverse rotation function of the reverse rotation mechanism. Therefore, the difference in rotational speed between the first drive shaft and the second drive shaft can be efficiently absorbed. The torque vector distribution device of the present invention can be mounted on a vehicle as a differential device in a drive system of the vehicle, for example.

The torque vector distribution device of the present invention is provided with an actuator for applying a control torque to each differential reaction element of the differential mechanism. Therefore, in addition to the function as the differential device as described above, the distribution ratio of the torques to the first drive shaft and the second drive shaft and the differential rotation between the first drive shaft and the second drive shaft can be actively controlled by the control torque output from the actuator. That is, torque vector distribution to the first drive shaft and the second drive shaft can be performed.

In the torque vector distribution device of the present invention, the reversing mechanism is disposed on the same rotation axis as the first drive shaft and the second drive shaft. The reversing mechanism basically has a so-called single-shaft structure in which the main rotating element is disposed on the same rotation axis as the first drive shaft and the second drive shaft. Therefore, the main part of the torque vector distribution device is constituted by a single-shaft structure. Therefore, the reversing mechanism can be easily provided while suppressing the radial increase in size of the torque vector distribution device. Further, the reverse function of rotating the first drive shaft and the second drive shaft in the directions opposite to each other is achieved by making the gear ratio of the first gear train in the first control planetary gear mechanism and the gear ratio of the second gear train in the second control planetary gear mechanism different from each other. For example, the gear ratio of the first gear train can be easily made different from the gear ratio of the second gear train by increasing (or decreasing) the number of teeth of the first gear relative to the number of teeth of the predetermined gear as a reference and by decreasing (or increasing) the number of teeth of the second gear relative to the number of teeth of the predetermined gear as a reference. Therefore, the reversing mechanism in the torque vector distribution device of the present invention can be easily configured without using a complicated configuration.

Further, in the torque vector distribution device of the present invention, as described above, the gear ratio of the first gear train in the first control planetary gear mechanism and the gear ratio of the second gear train in the second control planetary gear mechanism are made different from each other. Therefore, when the first control planetary gear mechanism and the second control planetary gear mechanism transmit torque, respectively, in a state where the rotational speeds of the left and right drive shafts are equal, the meshing of the gears in the first gear train and the meshing of the gears in the second gear train interfere with each other. As a result, the reversing mechanism is substantially engaged and integrally rotated. Therefore, the first drive shaft and the second drive shaft rotate integrally without performing differential rotation. In contrast, in a state where there is a difference in rotational speed between the rotational speed of the first drive shaft and the rotational speed of the second drive shaft, the engagement state due to the interference of the gears between the first gear train and the second gear train as described above is released, and the first control planetary gear mechanism and the second control planetary gear mechanism transmit torque according to the gear ratios of the first gear train and the second gear train, respectively. As a result, the first drive shaft and the second drive shaft rotate so that one drive shaft rotates in reverse direction with respect to the other drive shaft. That is, the first drive shaft and the second drive shaft perform differential rotation and rotate relatively in opposite rotational directions to each other. As described above, the torque vector distribution device of the present invention functions as a differential device that distributes and transmits the power torque input from the power source to the left and right drive shafts and absorbs the difference in rotational speed between the first drive shaft and the second drive shaft. In addition to this, by controlling the actuator to change the control torque, it is possible to realize torque vector distribution that controls the torque distribution to the first drive shaft and the second drive shaft.

Further, in the torque vector distribution device of the present invention, the first control planetary gear mechanism and the second control planetary gear mechanism in the reversing mechanism each form a reduction gear mechanism having a reduction ratio larger than "1". That is, the reversing mechanism has a deceleration function of amplifying the control torque of the actuator in addition to the reversing function described above. Therefore, according to the torque vector distribution device of the present invention, the actuator can be downsized in accordance with the enlargement of the control torque by the deceleration function of the reversing mechanism. Therefore, the torque vector distribution device can be miniaturized.

As described above, in the torque vector distribution device of the present invention, the reversing mechanism has a single-shaft structure, and the reversing mechanism can be easily configured without using a complicated structure. Further, by disposing the reversing mechanism coaxially with the first drive shaft and the second drive shaft, the torque vector distribution device can be prevented from being increased in size in the radial direction. Further, the actuator can be downsized by the deceleration function (torque amplification action) of the reversing mechanism. Therefore, according to the torque vector distribution device of the present invention, the inversion mechanism and the actuator can be easily downsized, and the outer shape of the torque vector distribution device can be downsized. As a result, the downsized torque vector distribution device can be easily mounted on the vehicle.

Further, the torque vector distribution device of the present invention can use an electric motor or a brake mechanism as the actuator. By controlling the electric motor to change the control torque, the differential rotation between the first drive shaft and the second drive shaft can be controlled. Alternatively, the differential rotation between the first drive shaft and the second drive shaft can be controlled by changing the control torque by controlling the brake mechanism. Further, the differential rotation between the first drive shaft and the second drive shaft can be restricted by the regenerative torque of the electric motor or the braking torque of the brake mechanism (differential lock).

The torque vector distribution device of the present invention can use an electric motor, a brake mechanism, or an electric motor with a brake function as a power source. The electric motor can output a drive torque as a power torque, controlling the drive force distribution between the first drive shaft and the second drive shaft. Further, the electric motor can also output regenerative torque as motive torque and control the braking force distribution between the first drive shaft and the second drive shaft. The braking force distribution by the regenerative braking of the electric motor can be executed with high accuracy and good responsiveness, and therefore, can be applied to, for example, ABS (Antilock Brake System) control of a vehicle. Further, by integrally assembling the electric motor and the torque vector distribution device of the present invention, the motor drive unit having the torque vector distribution function as described above can be configured. Alternatively, by integrally assembling the brake mechanism and the torque vector distribution device of the present invention, a brake unit having the torque vector distribution function as described above can be configured. Alternatively, by integrally assembling the electric motor with a braking function and the torque vector distribution device of the present invention, a power unit having the torque vector distribution function and the braking function as described above can be configured.

Drawings

Fig. 1 is a diagram for explaining an example (first embodiment) of a torque vector distribution device according to the present invention.

Fig. 2 is a diagram for explaining another example (second embodiment) of the torque vector distribution device according to the present invention.

Fig. 3 is a diagram for explaining another example (third embodiment) of the torque vector distribution device according to the present invention.

Fig. 4 is a diagram for explaining another example (fourth embodiment) of the torque vector distribution device according to the present invention.

Fig. 5 is a diagram for explaining another example (fifth embodiment) of the torque vector distribution device according to the present invention.

Fig. 6 is a diagram for explaining another example (sixth embodiment) of the torque vector distribution device according to the present invention.

Fig. 7 is a diagram for explaining another example (seventh embodiment) of the torque vector distribution device according to the present invention.

Fig. 8 is a diagram for explaining another example (eighth embodiment) of the torque vector distribution device according to the present invention.

Fig. 9 is a diagram for explaining another example (ninth embodiment) of the torque vector distribution device according to the present invention.

Fig. 10 is a diagram for explaining another example (tenth embodiment) of the torque vector distribution device according to the present invention.

Fig. 11 is a diagram for explaining another example (eleventh embodiment) of the torque vector distribution device according to the present invention.

Fig. 12 is a diagram for explaining another example (twelfth embodiment) of the torque vector distribution device according to the present invention.

Fig. 13 is a diagram for explaining another example (thirteenth embodiment) of the torque vector distribution device according to the present invention.

Fig. 14 is a diagram for explaining another example (fourteenth embodiment) of the torque vector distribution device according to the present invention.

Fig. 15 is a diagram for explaining another example (fifteenth embodiment) of the torque vector distribution device according to the present invention.

Fig. 16 is a diagram for explaining another example (sixteenth embodiment) of the torque vector distribution device according to the present invention.

Fig. 17 is a diagram for explaining another example (seventeenth embodiment) of the torque vector distribution device according to the present invention.

Fig. 18 is a diagram for explaining another example (eighteenth embodiment) of the torque vector distribution device of the present invention.

Fig. 19 is a diagram for explaining another example (nineteenth embodiment) of the torque vector distribution device according to the present invention.

Fig. 20 is a diagram for explaining another example (twentieth embodiment) of the torque vector distribution device according to the present invention.

Fig. 21 is a diagram for explaining another example (twenty-first embodiment) of the torque vector distribution device according to the present invention.

Fig. 22 is a diagram for explaining another example (a twenty-second embodiment) of the torque vector distribution device according to the present invention.

Description of the reference numerals

1. 41, 101: an input member; 2. 102: a differential mechanism; 3. 103: a first drive shaft; 4. 104: a second drive shaft; 5. 105: an actuator; 5a, 105 a: controlling a torque output shaft; 105 b: a first rotating shaft; 105 c: a second rotation shaft; 6. 106: a reversing mechanism; 7. 107: a housing (of the torque vector distribution device); 8. 108: an electric motor (power source); 8a, 108 a: a power torque output shaft; 108 b: a first power torque output shaft; 108 c: a second power torque output shaft; 9: a brake mechanism (power source); 10: a pinion (input gear); 11. 163, 166: a counter gear; 12: a counter gear shaft; 13. 43, 51, 62: a differential ring gear; 14: a differential housing; 15. 109, 141, 161, 201: a first power planetary gear mechanism; 16. 110, 142, 162, 202: a second power planetary gear mechanism; 17. 111: a power input element; 18. 112, 112: a first power output element; 19. 113: a first differential reaction force element; 20. 114: a second power output element; 21. 115: a second differential reaction force element; 22. 81, 121, 146, 169, 181, 211, 231, 251, 271, 291: a first planetary gear; 23. 82, 124, 147, 170, 182, 212, 232, 252, 272, 292: a second planetary gear; 24. 83, 126, 148, 171, 183, 213, 233, 253, 273: a third planetary gear; 25. 128, 149, 172, 185, 215, 234, 254, 274, 293: a first sun gear; 26. 129, 150, 173, 186, 216, 235, 255, 275, 294: a second sun gear; 27. 130, 151, 174, 187, 217, 236, 256, 276, 295: a third sun gear; 28. 89, 132, 152, 175: a wheel carrier; 29. 117, 311, 321, 331: a first control planetary gear mechanism; 30. 118, 312, 322, 332: a second control planetary gear mechanism; 31. 119: a control input element; 32. 120: a first control output element; 33. 122: a first gear; 34. 123: a second control output element; 35. 125: a second gear; 36. 66, 72, 90, 133, 153, 176, 196, 226, 243, 263, 280, 299: a first gear train; 37. 67, 73, 91, 134, 154, 177, 197, 227, 244, 264, 281, 300: a second gear train; 42: an input gear; 52. 277: a ring gear; 61: a reduction gear; 63. 85, 189, 219, 237, 257, 295: a first ring gear; 64. 86, 190, 220, 238, 258, 296: a second ring gear; 65. 87, 191, 221, 239, 259: a third ring gear; 71: a reduction planetary gear mechanism; 74: a reduction mechanism (compound planetary gear mechanism); 84. 127, 184, 214: a fourth planetary gear; 88. 192, 222: a fourth ring gear; 116. 203: a connecting shaft; 131. 188, 218: a fourth sun gear; 143: a first output torque reduction mechanism; 144: a connecting mechanism; 145: a second output torque reduction mechanism; 164: a first pinion gear; 165: a gear train; 167: a second pinion gear; 193. 223, 240, 260, 278, 297: a first wheel carrier; 194. 224, 241, 261, 279, 298: a second wheel carrier; 195. 225, 242, 262: a third wheel carrier; 282. 283, 301, 302: a gear transmission path; AL: a rotation axis; TV: and a torque vector distribution device.

Detailed Description

Embodiments of the present invention will be described with reference to the accompanying drawings. The embodiments described below are merely examples of embodying the present invention, and do not limit the present invention.

[ first embodiment ]

Fig. 1 shows an example (first embodiment) of a torque vector distribution device to which the present invention is applied. The torque vector distribution device TV according to the embodiment of the present invention includes, as main constituent elements, an input member 1, a differential mechanism 2, a first drive shaft 3, a second drive shaft 4, an actuator 5, and a reversing mechanism 6.

The input member 1 receives a power torque output from a predetermined power source. In the example shown in fig. 1, the input member 1 is a rotary shaft provided with an input gear (a pinion 10 described later), and both end portions are rotatably supported by the housing 7 of the torque vector distribution device TV.

A power torque output shaft 8a, which is an output shaft of the electric motor 8, is coupled to one end (right side in fig. 1) of the input member 1. A rotary shaft 9a of the brake mechanism 9 is coupled to the other end (left side in fig. 1) of the input member 1. That is, in the example shown in fig. 1, as a power source, an electric motor with a brake function is incorporated in the torque vector distribution device TV and unitized. The electric motor 8 generates a driving torque or a regenerative torque as a motive torque. The electric motor 8 is constituted by, for example, a permanent magnet type synchronous motor or an induction motor. The brake mechanism 9 generates a braking torque as a power torque. The brake mechanism 9 is configured by, for example, an excitation type electromagnetic brake that brakes a predetermined rotating member by magnetic attraction force generated by energization, an electric brake that generates frictional braking force using a feed screw mechanism driven by an electric motor, a regenerative brake that brakes a predetermined rotating member by resistance generated when power is generated by a motor, or the like.

By integrally assembling the electric motor 8 and the brake mechanism 9 together with the torque vector distribution device TV according to the embodiment of the present invention, a power unit having a torque vector distribution function and a brake function can be configured. The torque vector distribution device TV according to the embodiment of the present invention may be configured to incorporate only an electric motor as a power source. In this case, a motor drive unit having a torque vector distribution function can be configured. Alternatively, only the brake mechanism may be incorporated as the power source. In this case, a brake unit having a torque vector distribution function can be configured.

A pinion 10 is fitted to a central portion of the input member 1. The pinion 10 rotates integrally with the input member 1. The pinion gear 10 is a so-called input gear to which power torque is transmitted from a power source such as the electric motor 8 or the brake mechanism 9 via the input member 1. The pinion 10 meshes with a counter gear 11. The counter gear 11 is rotatably supported by a counter gear shaft 12. Both ends of the counter gear shaft 12 are fixed to the housing 7. Furthermore, the counter gear 11 and the pinion 10 mesh together with the differential ring gear 13. The differential ring gear 13 is an externally toothed gear provided at an outer peripheral portion of the differential case 14. The differential ring gear 13 rotates integrally with the differential case 14. A third sun gear shaft 27a, which will be described later, is coupled to the differential case 14. Therefore, the differential case 14 and the differential ring gear 13 rotate integrally with the third sun gear shaft 27 a. The differential case 14 accommodates the differential mechanism 2, the reversing mechanism 6, and the like therein. The differential case 14 is supported by the case 7 so as to be rotatable with respect to the case 7. In the example shown in fig. 1, the differential case 14 is supported to be rotatable relative to the case 7 and a carrier shaft 28b described later.

The counter gear 11 and the differential ring gear 13 are both large-diameter gears having a larger diameter than the pinion gear 10 and having a larger number of teeth than the pinion gear 10. Therefore, the gear train constituted by the pinion gear 10, the counter gear 11, and the differential ring gear 13 forms a reduction gear mechanism that reduces the output rotation speed of the differential ring gear 13 relative to the input rotation speed of the pinion gear 10. Therefore, the motive torque of the motive power source input to the input member 1 is amplified by the transmission gear mechanism including the pinion gear 10, the counter gear 11, and the differential ring gear 13 as described above, and is transmitted to the motive power input element 17 of the differential mechanism 2 described later.

The differential mechanism 2 is constituted by a first power planetary gear mechanism 15 and a second power planetary gear mechanism 16. The first power planetary gear mechanism 15 and the second power planetary gear mechanism 16 are disposed coaxially and in a left-right opposed manner. The first power planetary gear mechanism 15 has a power input element 17, a first power output element 18, and a first differential reaction element 19. The power input element 17 is transmitted with power torque from the input member 1. The first power output element 18 outputs power torque to the first driveshaft 3. The control torque, which will be described later, is transmitted to the first differential reaction element 19 as a reaction force to the power torque transmitted from the power input element 17 to the first power output element 18. On the other hand, the second power planetary gear mechanism 16 has a power input element 17, a second power output element 20, and a second differential reaction element 21. The power input element 17 is used in combination with the first power planetary gear mechanism 15 described above. The second power output element 20 outputs power torque to the second drive shaft 4. The control torque, which will be described later, is transmitted to the second differential reaction element 21 as a reaction force to the power torque transmitted from the power input element 17 to the second power output element 20. In the example shown in fig. 1, a carrier 28, which will be described later, serves as both the first differential reaction element 19 and the second differential reaction element 21.

The differential mechanism 2 includes: three sets of planetary gears of a first planetary gear 22, a second planetary gear 23, and a third planetary gear 24; three sun gears, a first sun gear 25, a second sun gear 26, and a third sun gear 27; and a wheel carriage 28. The first planetary gear 22, the second planetary gear 23, and the third planetary gear 24 are coaxially arranged in series. The first sun gear 25, the second sun gear 26, and the third sun gear 27 are coaxially arranged in series. The carrier 28 holds the first planetary gears 22, the second planetary gears 23, and the third planetary gears 24 rotatably and revolvably around the sun gears 25, 26, and 27, respectively.

The first planetary gears 22, the second planetary gears 23, and the third planetary gears 24 are rotatably supported by planetary gear shafts 28a fixed to a carrier 28. The first planetary gears 22, the second planetary gears 23, and the third planetary gears 24 all rotate integrally in a rotation direction about the planetary gear shafts 28a (do not rotate relative to each other in the rotation direction). The first planetary gears 22 mesh with a first sun gear 25. The second planetary gears 23 mesh with a second sun gear 26. The third planetary gears 24 mesh with a third sun gear 27. The first sun gear 25, the second sun gear 26, and the third sun gear 27 are rotatably supported by the housing 7 so as to be rotatable relative to each other.

A third sun gear shaft 27a that rotates integrally with the third sun gear 27 is fitted to the differential case 14. The third sun gear shaft 27a rotates integrally with the differential case 14. That is, the third sun gear 27 rotates integrally with the differential ring gear 13. Thus, the motive torque generated by the motive power source is transmitted to the third sun gear 27 via the input member 1 and the speed change gear mechanism including the pinion gear 10, the counter gear 11, and the differential ring gear 13. Therefore, the third sun gear 27 serves as the power input element 17 of the differential mechanism 2.

The first sun gear 25 is coupled to the first drive shaft 3. The first sun gear 25 rotates integrally with the first drive shaft 3. Therefore, a part of the power torque transmitted to the differential mechanism 2 is output from the first sun gear 25 to the first drive shaft 3. Therefore, the first sun gear 25 becomes the first power output element 18 of the differential mechanism 2.

The second sun gear 26 is coupled to the second drive shaft 4. The second sun gear 26 rotates integrally with the second drive shaft 4. Therefore, a part of the power torque transmitted to the differential mechanism 2 is output from the second sun gear 26 to the second drive shaft 4. Therefore, the second sun gear 26 serves as the second power output element 20 of the differential mechanism 2.

A carrier shaft 28b that rotates integrally with the carrier 28 is coupled to a control torque output shaft 5a of the actuator 5 described later. The carrier 28 rotates integrally with the control torque output shaft 5 a. As described below, the control torque transmitted from the actuator 5 to the carrier 28 acts as a reaction force against the power torque transmitted from the power input element 17 to the first power output element 18 and the power torque transmitted from the power input element 17 to the second power output element 20. Therefore, the carrier 28 serves as the first differential reaction element 19 and the second differential reaction element 21 of the differential mechanism 2.

In this way, in the differential mechanism 2, the third sun gear 27 serves as the power input element 17, the first sun gear 25 serves as the first power output element 18, and the carrier 28 serves as the first differential reaction element 19, thereby constituting the first power planetary gear mechanism 15. At the same time, the third sun gear 27 serves as the power input element 17, the second sun gear 26 serves as the second power output element 20, and the carrier 28 serves as the second differential reaction element 21, thereby constituting the second power planetary gear mechanism 16.

The first and second differential reaction force elements 19, 21 (i.e., the carrier 28) are supported by reaction forces at the time of rotation of the power input element 17 and the first and second

power output elements

18, 20 so that a difference in rotation speed between the first and second

power output elements

18, 20 is allowed when power torque is transmitted from the power input element 17 (i.e., the third sun gear 27) to the first and second power output elements 18, 20 (i.e., the first and second sun gears 25, 26).

The first drive shaft 3 and the second drive shaft 4 are coaxially arranged to face left and right. Further, the first drive shaft 3 and the second drive shaft 4 are disposed coaxially with the first power planetary gear mechanism 15 and the second power planetary gear mechanism 16. Specifically, the first and

second drive shafts

3 and 4 and the first and second power planetary gear mechanisms 15 and 16 are arranged on the same rotation axis AL. The first drive shaft 3 and the second drive shaft 4 are rotatable relative to each other. The end of the first drive shaft 3 on the projecting side (left side in fig. 1) is rotatably supported by the housing 7. Similarly, the end of the second drive shaft 4 on the protruding side (the right side in fig. 1) is rotatably supported by the housing 7. For example, when the torque vector distribution device TV according to the embodiment of the present invention is mounted on a vehicle, drive wheels (not shown) are mounted on the first drive shaft 3 and the second drive shaft 4, respectively.

The first driveshaft 3 and the second driveshaft 4 are coupled to a first power output element 18 and a second power output element 20, respectively, of the differential mechanism 2. Therefore, the first driveshaft 3 and the second driveshaft 4 are differentially rotated by the action of the differential mechanism 2. For example, when a vehicle equipped with the torque vector distribution device TV according to the embodiment of the present invention is turning, the differential mechanism 2 functions as a differential device of the vehicle, and the first drive shaft 3 and the second drive shaft 4 are differentially rotated according to a difference in rotation speed between the inner wheel and the outer wheel. Further, as described below, when the control torque of the actuator 5 is changed to control the torque distribution to the left and right drive wheels, that is, when the torque vector distribution is performed, the first drive shaft 3 and the second drive shaft 4 perform differential rotation.

The actuator 5 gives the torque generated by the actuator 5 to the differential mechanism 2 as a control torque. The differential mechanism 2 differentially rotates the first drive shaft 3 and the second drive shaft 4 by the first differential reaction element 19 and the second differential reaction element 21 of which control torques are applied to the differential mechanism 2. As the actuator 5, for example, an electric motor or a brake mechanism can be used. The electric motor outputs, as control torque, drive torque that drives the first differential reaction element 19 and the second differential reaction element 21. Alternatively, regenerative torque that brakes the first differential reaction element 19 and the second differential reaction element 21 is output as control torque. The brake mechanism outputs, as a control torque, a braking torque that brakes the first differential reaction element 19 and the second differential reaction element 21. For example, an excitation type electromagnetic brake that brakes a predetermined rotating member by magnetic attraction force generated by energization, an electric brake that generates friction braking force by using a feed screw mechanism driven by an electric motor, or the like may be used.

The actuator 5 has a control torque output shaft 5a that outputs the drive torque, the regenerative torque, or the brake torque as the control torque. In the example shown in fig. 1, an electric motor that outputs a drive torque or a regenerative torque as a control torque is used. Therefore, the rotor shaft of the electric motor becomes the control torque output shaft 5 a. The control torque output shaft 5a is coupled to a carrier shaft 28b of the carrier 28. The carrier 28 rotates integrally with the control torque output shaft 5 a.

As described above, in the torque vector distribution device TV according to the embodiment of the present invention, an electric motor or a brake mechanism may be used as the actuator 5. By controlling the electric motor to change the control torque, the differential rotation between the first drive shaft 3 and the second drive shaft 4 can be controlled. Alternatively, the differential rotation between the first drive shaft 3 and the second drive shaft 4 can be controlled by changing the control torque by controlling the brake mechanism. Further, the differential rotation between the first drive shaft 3 and the second drive shaft 4 can be restricted by the regenerative torque of the electric motor or the braking torque of the brake mechanism (differential lock).

The reversing mechanism 6 is disposed coaxially with the first drive shaft 3 and the second drive shaft 4. The reverse rotation mechanism 6 rotates the first driveshaft 3 and the second driveshaft 4 in opposite directions when the first driveshaft 3 and the second driveshaft 4 rotate differentially. The reversing mechanism 6 is constituted by a first control planetary gear mechanism 29 and a second control planetary gear mechanism 30. The first control planetary gear mechanism 29 and the second control planetary gear mechanism 30 are each disposed coaxially with the first drive shaft 3 and the second drive shaft 4. Specifically, the first and

second drive shafts

3, 4 and the first and second control planetary gear mechanisms 29, 30 are all arranged on the same rotation axis AL. The first control planetary gear mechanism 29 transmits the control torque output by the actuator 5 to the first drive shaft 3 via the first differential reaction element 19 of the differential mechanism 2. The second control planetary gear mechanism 30 transmits the control torque output by the actuator 5 to the second drive shaft 4 via the second differential reaction element 21 of the differential mechanism 2.

The reversing mechanism 6 is configured to: when the first drive shaft 3 and the second drive shaft 4 rotate in the same direction and at the same speed, they rotate together with the power input element 17 (i.e., the third sun gear 27) and the first power output element 18 (i.e., the first sun gear 25) and the second power output element 20 (i.e., the second sun gear 26).

The first control planetary gear mechanism 29 has a control input member 31, a first control output member 32, first planetary gears 22, and first gears 33. The control input member 31 is inputted with a control torque from the actuator 5. The first control output member 32 outputs a control torque to the first drive shaft 3. In the reversing mechanism 6, the first planetary gear 22 is transmitted with the control torque from the control input element 31. The first gear 33 meshes with the first planetary gears 22, forming the control input member 31 or the first control output member 32. On the other hand, the second control planetary gear mechanism 30 has a control input element 31, a second control output element 34, second planetary gears 23, and second gears 35. The control input element 31 is shared with the first control planetary gear mechanism 29 described above. The second control output member 34 outputs a control torque to the second drive shaft 4. In the reversing mechanism 6, the second planetary gear 23 is transmitted with the control torque from the control input member 31. The second gear 35 meshes with the second planetary gears 23, forming the control input member 31 or the second control output member 34.

The reversing mechanism 6 has: three sets of planetary gears of a first planetary gear 22, a second planetary gear 23, and a third planetary gear 24; three sun gears, a first sun gear 25, a second sun gear 26, and a third sun gear 27; and a wheel carriage 28. The carrier 28 serves as a control input element 31, and the first sun gear 25 serves as a first control output element 32, thereby constituting a first control planetary gear mechanism 29. In this case, the first sun gear 25 meshing with the first planetary gears 22 serves as the first control output element 32 and serves as the first gear 33. The carrier 28 serves as a control input element 31, and the second sun gear 26 serves as a second control output element 34, thereby constituting a second control planetary gear mechanism 30. In this case, the second sun gear 26 meshing with the second planetary gears 23 is the second control output element 34, and is the second gear 35.

The gear ratios of the first gear train 36 including the first planetary gears 22 and the first gears 33 and the gear ratios of the second gear train 37 including the second planetary gears 23 and the second gears 35 are different from each other. Specifically, the gear ratios of the gear pairs of the first planetary gears 22 and the first sun gear 25 in the first gear train 36 and the gear ratios of the gear pairs of the second planetary gears 23 and the second sun gear 26 in the second gear train 37 are different from each other. In the example shown in fig. 1, the number of teeth of the first sun gear 25, the number of teeth of the second sun gear 26, and the number of teeth of the third sun gear 27 are all equal. The number of teeth of the first planetary gear 22, the number of teeth of the second planetary gear 23, and the number of teeth of the third planetary gear 24 are each less than the number of teeth of each sun gear 25, 26, 27. Also, the number of teeth of the first planetary gears 22 is greater than that of the third planetary gears 24, and the number of teeth of the second planetary gears 23 is less than that of the third planetary gears 24. For example, as indicated by the parenthesized numerical values in fig. 1, the number of teeth of each sun gear 25, 26, 27 is "68", the number of teeth of the first planetary gear 22 is "36", the number of teeth of the second planetary gear 23 is "34", and the number of teeth of the third planetary gear 24 is "35".

In this case, when the number of teeth of the first planetary gear 22 is set to z_P1Z represents the number of teeth of the first sun gear 25_S1In time, the gear ratio u of the first gear train 36₁The method comprises the following steps:

u₁＝z_P1/z_S1。

therefore, for example, as in the above example, the number of teeth z of the first planetary gear 22_P136', the number of teeth z of the first sun gear 25_S1At "68", the gear ratio u of the first gear train 36₁The method comprises the following steps:

u₁＝0.53。

similarly, when the number of teeth of the second planetary gear 23 is z_P2Z is the number of teeth of the second sun gear 26_S2The gear ratio u of the second gear train 37₂The method comprises the following steps:

u₂＝z_P2/z_S2。

therefore, for example, as in the above example, the number of teeth z of the second planetary gear 23_P234', number of teeth z of second sun gear 26_S2At "68", the gear ratio u of the second gear train 37₂The method comprises the following steps:

u₂＝0.50。

the number z of teeth of the first planetary gear 22_P1Number z of teeth with the second planetary gear 23_P2Are different from each other, whereby the gear ratio u of the first gear train 36₁With gear ratio u of the second gear train 37₂Are different from each other.

As described above, the gear ratio u of the first gear train 36 in the first control planetary gear mechanism 29₁Gear ratio u to the second gear train 37 in the second control planetary gear mechanism 30 ₂Different from each other, therefore, in a state where the rotation speed of the first drive shaft 3 is equal to the rotation speed of the second drive shaft 4, when the first control planetary gear mechanism 29 and the second control planetary gear mechanism 30 transmit torque, respectively, the first gear train 36 in the first control planetary gear mechanism 29 and the second gear train 37 in the second control planetary gear mechanism 30 interfere with each other. In the example shown in FIG. 1, the number of teeth z of the first planetary gears 22 in the first gear train 36_P1(36) Number z of teeth of third planetary gear 24 in gear train including third sun gear 27 and third planetary gear 24_P3(35) One more tooth, thereby the first sun gear 2 in the first gear train 365 are intended to rotate one tooth faster than the third sun gear 27. On the other hand, the number z of teeth of the second planetary gears 23 in the second gear train 37_P2(34) Is less than the number z of teeth of the third planetary gear 24 in the gear train of the third sun gear 27 and the third planetary gear 24_P3(35) One tooth less, so that the second sun gear 26 in the second gear train 37 is intended to rotate one tooth slower than the third sun gear 27. Therefore, the first sun gear 25 and the second sun gear 26 are intended to rotate relatively in opposite directions to each other. In this case, the first planetary gears 22 meshing with the first sun gear 25 rotate and revolve integrally with the second planetary gears 23 meshing with the second sun gear 26, and do not rotate relative to each other in the rotation direction and the revolution direction. Therefore, torques in opposite directions to each other act on the meshing portion of the first gear train 36 and the meshing portion of the second gear train 37, so that the first gear train 36 and the second gear train 37 interfere with each other. As a result, the reversing mechanism 6 is substantially engaged and integrally rotated. Therefore, the first driveshaft 3 and the second driveshaft 4 rotate integrally without performing differential rotation.

In contrast, in a state where there is a difference in rotational speed between the rotational speed of the first driveshaft 3 and the rotational speed of the second driveshaft 4, the substantial engagement state of the reversing mechanism 6 due to the interference of the gears between the first gear train 36 and the second gear train 37 as described above is released, and the first control planetary gear mechanism 29 and the second control planetary gear mechanism 30 are each released in accordance with the gear ratio u of the first gear train 36₁And the gear ratio u of the second gear train 37₂To transmit torque. In the example shown in fig. 1, the first gear train 36 and the second gear train 37 perform differential rotation, and thereby the substantial engagement state of the reversing mechanism 6 is released. In this case, as described above, the torques in the opposite directions to each other act on the meshing portion of the first gear train 36 and the meshing portion of the second gear train 37. Therefore, the first sun gear 25 and the second sun gear 26 relatively rotate in opposite directions to each other. That is, the first sun gear 25 and the second sun gear 26 rotate so that the second sun gear 26 rotates in reverse with respect to the first sun gear 25. As a result, the first drive shaft 3 and the second drive shaft 4 are driven by one drive shaft 3 (or 4) with respect to the otherThe shafts 4 (or 3) rotate in reverse directions, respectively. That is, the first drive shaft 3 and the second drive shaft 4 perform differential rotation and rotate relatively in opposite directions to each other.

Also, the reversing mechanism 6 is configured to: a first reduction ratio representing the proportion of the rotational speed of the first control output member 32 relative to the rotational speed of the control input member 31 and a second reduction ratio representing the proportion of the rotational speed of the second control output member 34 relative to the rotational speed of the control input member 31 are both greater than "1". In the example shown in fig. 1, it is configured such that a first reduction ratio between the carrier 28 and the first sun gear 25 and a second reduction ratio between the carrier 28 and the second sun gear 26 are both greater than "1". Therefore, the first control planetary gear mechanism 29 and the second control planetary gear mechanism 30 form a reduction gear mechanism that reduces the output rotational speed of the first sun gear 25 and the second sun gear 26 relative to the input rotational speed of the carrier 28, respectively. Therefore, as described below, the first control planetary gear mechanism 29 and the second control planetary gear mechanism 30 amplify the control torque of the actuator 5 input to the carrier 28 and transmit the amplified control torque to the first drive shaft 3 side and the second drive shaft 4 side.

For example, as in the above example, the number of teeth z of the first planetary gear 22_P136', the number of teeth z of the first sun gear 25_S1Is "68", the number of teeth z of the second planetary gear 23_P234', number of teeth z of second sun gear 26 _S2Is "68", the number of teeth z of the third planetary gear 24_P335', the number of teeth z of the third sun gear 27_S3At "68", the first reduction gear ratio R of the first control planetary gear mechanism 29₁And a second reduction gear ratio R of the second control planetary gear mechanism 30₂Respectively become:

R₁＝1/{1－(z_S3/z_P3)×(z_P1/z_S1)}≈35；

R₂＝1/{1－(z_S3/z_P3)×(z_P2/z_S2)}≈－35。

a relatively large reduction ratio is obtained compared to the reduction ratio that can be achieved with a conventional general planetary gear mechanism, which is approximately 4 to 10 or so.

In the first control planetary gear mechanism 29, the rotational direction of the first differential reaction element 19 (i.e., the carrier 28) of the differential mechanism 2 and the rotational direction of the first power output element 18 (i.e., the first sun gear 25) of the differential mechanism 2 are the same rotational direction, and the control torque is transmitted between the first differential reaction element 19 and the first power output element 18. On the other hand, in the second control planetary gear mechanism 30, the rotation direction of the second power output element 20 (i.e., the second sun gear 26) of the differential mechanism 2 is reversed with respect to the rotation direction of the second differential reaction element 21 (i.e., the carrier 28) of the differential mechanism 2, and the control torque is transmitted between the second differential reaction element 21 and the second power output element 20. Therefore, if the rotational direction of the first power output element 18 in the first control planetary gear mechanism 29 is set to the positive rotational direction, the rotational direction of the second power output element 20 in the second control planetary gear mechanism 30 becomes the negative rotational direction or the reverse rotational direction. Therefore, in the description of the embodiment of the present invention, for convenience, the second reduction gear ratio R of the second control planetary gear mechanism 30 is set ₂The sign of minus (-) is noted. In the example shown in fig. 1, the reduction ratio R between the actuator 5 and the first and

second drive shafts

3 and 4 in the reversing mechanism 6 is represented as "R ═ 35".

As described above, in the torque vector distribution device TV according to the embodiment of the present invention, the first control planetary gear mechanism 29 and the second control planetary gear mechanism 30 in the reversing mechanism 6 each form a reduction gear mechanism having a reduction ratio larger than "1". That is, the reversing mechanism 6 has a reversing function of relatively rotating the first drive shaft 3 and the second drive shaft 4 in opposite rotational directions to each other when the first drive shaft 3 and the second drive shaft 4 are differentially rotated, and also has a speed reducing function (torque amplifying function) of amplifying the control torque of the actuator 5. In the example shown in fig. 1, the torque amplification function is provided, which has a large reduction gear ratio of "35". Therefore, according to the torque vector distribution device TV of the embodiment of the present invention, the actuator 5 can be downsized in accordance with the enlargement of the control torque by the deceleration function of the reversing mechanism 6. Therefore, the torque vector distribution device TV can be miniaturized.

In the torque vector distribution device TV according to the embodiment of the present invention, the reversing mechanism 6 has a single-shaft structure. Therefore, the reversing mechanism 6 having both the reversing function and the decelerating function as described above can be easily configured without using a complicated structure. Further, by disposing the reversing mechanism 6 coaxially with the first drive shaft 3 and the second drive shaft 4, the torque vector distribution device TV can be prevented from being increased in size in the radial direction. Further, the actuator 5 can be downsized by the deceleration function of the reversing mechanism 6. Therefore, according to the torque vector distribution device TV of the embodiment of the present invention, the inversion mechanism 6 and the actuator 5 can be easily downsized, and further, the outer shape of the torque vector distribution device TV can be downsized. As a result, the downsized torque vector distribution device TV can be easily mounted on the vehicle.

The order of arrangement of the first planetary gears 22, the second planetary gears 23, and the third planetary gears 24, and the first sun gear 25, the second sun gear 26, and the third sun gear 27 is not limited to the order shown in fig. 1. For example, the first planetary gear 22 and the first sun gear 25 may be disposed alternately with the second planetary gear 23 and the second sun gear 26. Alternatively, the third planetary gear 24 and the third sun gear 27 may be disposed on the right side of fig. 1.

Fig. 2 to 22 show other embodiments of a torque vector distribution device TV to which the present invention is applied. In the torque vector distribution device TV illustrated below, the same reference numerals as those used in fig. 1 or the already-shown drawings are given to members, components, and the like having the same configurations and functions as those of the torque vector distribution device TV illustrated in fig. 1 or the already-shown drawings.

[ second embodiment ]

The torque vector distribution device TV shown in fig. 2 is provided with an input member 41 instead of the input member 1 in the torque vector distribution device TV shown in fig. 1. The input member 41 receives a power torque output from a predetermined power source. The input member 41 is a rotary shaft provided with an input gear 42 described later, and is rotatably supported by the casing 7 of the torque vector distribution device TV in a rotation axis direction orthogonal to the rotation axis AL.

An input gear 42 is attached to one end (lower side in fig. 2) of the input member 41. The input gear 42 rotates integrally with the input member 41. In the example shown in fig. 2, the input gear 42 is a small-diameter bevel gear that meshes with a differential ring gear 43 described later. Motive torque is transmitted from the motive power source to the input gear 42 via the input member 41. The input gear 42 meshes with a differential ring gear 43. The differential ring gear 43 is a large-diameter bevel gear provided at the outer peripheral portion of the differential case 14. The differential ring gear 43 rotates integrally with the differential case 14. The input gear 42 and the differential ring gear 43 may be formed using a hypoid gear (hypoid gear), for example.

An output shaft of a power source such as the electric motor 8 and the brake mechanism 9 shown in fig. 1 is connected to the other end (upper side in fig. 2) of the input member 41. The constitution from the differential case 14 to the first drive shaft 3 and the second drive shaft 4 via the differential mechanism 2 and the reversing mechanism 6 is the same as the torque vector distribution device TV shown in fig. 1.

Thus, according to the torque vector distribution device TV shown in fig. 2, a differential device having a torque vector distribution function can be configured separately from the power source. Therefore, for example, the torque vector distribution device TV can be easily mounted on the vehicle as a differential device with a torque vector distribution function, instead of a conventional differential device in a conventional vehicle.

[ third embodiment ]

In the torque vector distribution device TV shown in fig. 3, the input gear 42 of the input member 41 meshes with the differential ring gear 51. The differential ring gear 51 is a large-diameter bevel gear corresponding to the input gear 42 (small-diameter bevel gear). The differential ring gear 51 is fitted to the third sun gear shaft 27a of the third sun gear 27. The differential ring gear 51 rotates integrally with the third sun gear shaft 27 a. Therefore, the motive torque generated by the motive power source is transmitted to the third sun gear 27 via the input member 41, the input gear 42, and the differential ring gear 51. Therefore, in the torque vector distribution device TV shown in fig. 3, the third sun gear 27 also serves as the power input element 17 of the differential mechanism 2.

The carrier 28 in the differential mechanism 2 is not linked to any rotating member. Therefore, the carrier 28 is in a freely rotatable state. The carrier 28 is supported to be rotatable relative to the third sun gear shaft 27a and the second drive shaft 4.

The differential mechanism 2 has an internal gear ring 52 meshing with the third planetary gears 24. A ring gear shaft 52a that rotates integrally with the ring gear 52 is coupled to the control torque output shaft 5a of the actuator 5. The ring gear 52 rotates integrally with the control torque output shaft 5 a. The torque of the ring gear 52 is transmitted to the first sun gear 25 and the second sun gear 26 via the third planetary gears 24 and the first planetary gears 22 and the second planetary gears 23. Therefore, the control torque transmitted from the actuator 5 to the ring gear 52 acts as a reaction force against the power torque transmitted from the power input element 17 (i.e., the third sun gear 27) to the first power output element 18 (i.e., the first sun gear 25) and the power torque transmitted from the power input element 17 to the second power output element 20 (i.e., the second sun gear 26). Therefore, the ring gear 52 serves as the first differential reaction element 19 and the second differential reaction element 21 of the differential mechanism 2.

As described above, the control torque of the actuator 5 is transmitted to the reversing mechanism 6 via the ring gear 52. Therefore, the reduction gear ratio R between the actuator 5 and the first and

second drive shafts

3, 4 in the reversing mechanism 6 can be increased as compared with a configuration in which the control torque of the actuator 5 is transmitted to the reversing mechanism 6 via the carrier 28 as in the torque vector distribution device TV shown in fig. 1.

For example, as in the above example, when the number of teeth of the first planetary gear 22 is "36", the number of teeth of the first sun gear 25 is "68", the number of teeth of the second planetary gear 23 is "34", the number of teeth of the second sun gear 26 is "68", the number of teeth of the third planetary gear 24 is "35", and the number of teeth of the third sun gear 27 is "68", the reduction gear ratio R in the torque vector distribution device TV shown in fig. 1 is "R ═ 35", whereas when the number of teeth of the ring gear 52 is "138", the reduction gear ratio R in the torque vector distribution device TV shown in fig. 3 is "R ═ 52". A reduction ratio of about 1.5 times as large as that of the torque vector distribution device TV shown in fig. 1 is obtained.

As described above, according to the torque vector distribution device TV shown in fig. 3, by adding the ring gear 52, which is a reaction element of the differential mechanism 2 and serves as an input member of the control torque of the actuator 5 to the reversing mechanism 6, a larger reduction gear ratio can be obtained as compared with the example shown in fig. 1 and 2. Therefore, the control torque of the actuator 5 can be amplified more. Therefore, the torque vector distribution device TV can be miniaturized by further miniaturizing the actuator 5.

[ fourth embodiment ]

In the torque vector distribution device TV shown in fig. 4, the pinion gear 10 fitted to the input member 1 is meshed with the large diameter gear 61a of the reduction gear 61. The reduction gear 61 has a large-diameter gear 61a and a small-diameter gear 61b which are coaxially arranged in series and integrally rotate, respectively. The large diameter gear 61a has a larger diameter than the pinion gear 10 and has a larger number of teeth than the pinion gear 10. The small-diameter gear 61b meshes with a differential ring gear 62 of an external gear provided on an outer peripheral portion of a third ring gear 65 described later. The small-diameter gear 61b has a smaller diameter than the differential ring gear 62 and has fewer teeth than the differential ring gear 62. Therefore, the gear train constituted by the pinion gear 10, the large diameter gear 61a, the small diameter gear 61b, and the differential ring gear 62 forms a reduction gear mechanism that reduces the output rotation speed of the differential ring gear 62 relative to the input rotation speed of the pinion gear 10. Therefore, the motive torque of the motive power sources (the electric motor 8 and the brake mechanism 9 in the example shown in fig. 4) input to the input member 1 is amplified by the transmission gear mechanism including the pinion gear 10, the reduction gear 61, and the differential ring gear 62 as described above, and is transmitted to the third ring gear 65 of the differential mechanism 2.

The differential mechanism 2 includes: three sets of planetary gears of a first planetary gear 22, a second planetary gear 23, and a third planetary gear 24; three ring gears of a first ring gear 63, a second ring gear 64, and a third ring gear 65; and a wheel carriage 28. The first planetary gear 22, the second planetary gear 23, and the third planetary gear 24 are coaxially arranged in series. The first ring gear 63, the second ring gear 64, and the third ring gear 65 are coaxially arranged in series. The first and second ring gears 63, 64 and 65 rotate relative to each other. The first planetary gears 22 are meshed with the first ring gear 63. The second planetary gears 23 mesh with the second ring gear 64. The third planetary gears 24 are meshed with the third ring gear 65.

The first ring gear 63 is coupled to the first drive shaft 3. The first ring gear 63 rotates integrally with the first drive shaft 3. The second ring gear 64 is coupled to the second drive shaft 4. The second ring gear 64 rotates integrally with the second drive shaft 4. The third ring gear 65 is coupled to the differential ring gear 62. The third ring gear 65 rotates integrally with the differential ring gear 62.

The carrier 28 is coupled to the control torque output shaft 5a of the actuator 5. The carrier 28 rotates integrally with the control torque output shaft 5 a. The torque of the carrier 28 is transmitted to the first ring gear 63 and the second ring gear 64 via the first planetary gears 22 and the second planetary gears 23. Therefore, the control torque transmitted from the actuator 5 to the carrier 28 acts as a reaction force against the power torque transmitted from the third ring gear 65 to the first ring gear 63 via the third planetary gears 24 and the first planetary gears 22 and the power torque transmitted from the third ring gear 65 to the second ring gear 64 via the third planetary gears 24 and the second planetary gears 23.

Therefore, the third ring gear 65 serves as the power input element 17 of the differential mechanism 2, the first ring gear 63 serves as the first power output element 18 of the differential mechanism 2, and the carrier 28 serves as the first differential reaction element 19 of the differential mechanism 2, thereby constituting the first power planetary gear mechanism 15. The third ring gear 65 serves as the power input element 17 of the differential mechanism 2, the second ring gear 64 serves as the second power output element 20 of the differential mechanism 2, and the carrier 28 serves as the second differential reaction element 21 of the differential mechanism 2, thereby constituting the second power planetary gear mechanism 16.

The reversing mechanism 6 has: three sets of planetary gears of a first planetary gear 22, a second planetary gear 23, and a third planetary gear 24; three ring gears of a first ring gear 63, a second ring gear 64, and a third ring gear 65; and a wheel carriage 28. The carrier 28 is coupled to the control torque output shaft 5a of the actuator 5. The first ring gear 63 is coupled to the first power output element 18 of the differential mechanism 2, i.e., the first driveshaft 3. The first ring gear 63 and the first planetary gears 22 mesh with each other. The second ring gear 64 is coupled to the second power output element 20 of the differential mechanism 2, i.e., the second driveshaft 4. The second ring gear 64 and the second planetary gears 23 mesh with each other.

Therefore, the carrier 28 serves as the control input element 31, and the first ring gear 63 serves as the first gear 33 and the first control output element 32, thereby constituting the first control planetary gear mechanism 29. The carrier 28 serves as the control input element 31, and the second ring gear 64 serves as the second gear 35 and the second control output element 34, thereby constituting the second control planetary gear mechanism 30.

In the example shown in fig. 4, the gear ratio of the first gear train 66 including the first planetary gears 22 and the first gear 33 (i.e., the first ring gear 63) and the gear ratio of the second gear train 67 including the second planetary gears 23 and the second gear 35 (i.e., the second ring gear 64) are different from each other. Specifically, the gear ratios of the gear pairs of the first planetary gears 22 and the first ring gear 63 in the first gear train 66 and the gear ratios of the gear pairs of the second planetary gears 23 and the second ring gear 64 in the second gear train 67 are different from each other.

More specifically, the number of teeth of the first ring gear 63, the number of teeth of the second ring gear 64, and the number of teeth of the third ring gear 65 are all equal. The number of teeth of the first planetary gears 22, the number of teeth of the second planetary gears 23, and the number of teeth of the third planetary gears 24 are each less than the number of teeth of each of the ring gears 63, 64, 65. Also, the number of teeth of the first planetary gears 22 is greater than that of the third planetary gears 24, and the number of teeth of the second planetary gears 23 is less than that of the third planetary gears 24. For example, as indicated by the parenthesized numerical values in fig. 4, the number of teeth of each of the ring gears 63, 64, 65 is "68", the number of teeth of the first planetary gear 22 is "36", the number of teeth of the second planetary gear 23 is "34", and the number of teeth of the third planetary gear 24 is "35". In this case, the reduction ratio R is "R ═ 35".

According to the torque vector distribution device TV shown in fig. 4, as in the example shown in fig. 1 and 2, the actuator 5 can be downsized in accordance with the enlargement of the control torque by the deceleration function of the reversing mechanism 6. Further, the reversing mechanism 6 of the single-shaft structure can be easily configured. Further, by disposing the reversing mechanism 6 coaxially with the first drive shaft 3 and the second drive shaft 4, the torque vector distribution device TV can be prevented from being increased in size in the radial direction. In addition, in the torque vector distribution device TV shown in fig. 4, the ring gears 63, 64, and 65 that mesh with the

planetary gears

22, 23, and 24 are provided, and thus an increase in the centrifugal force of the carrier 28 generated when the torque vector distribution device TV rotates can be suppressed by the ring gears 63, 64, and 65. Therefore, the strength of the carrier 28 can be reduced in design, and the differential mechanism 2 and the reversing mechanism 6 can be downsized accordingly. In the torque vector distribution device TV shown in fig. 4, the first and second power planetary gear mechanisms 15, 16 and the first and second control planetary gear mechanisms 29, 30 are each constituted by the respective

planetary gears

22, 23, 24, the carrier 28, and the respective ring gears 63, 64, 65. That is, the first and second power planetary gear mechanisms 15 and 16 and the first and second control planetary gear mechanisms 29 and 30 are configured without using a sun gear. Therefore, a space for disposing a sun gear having a larger diameter than the

planetary gears

22, 23, 24 and a larger number of teeth than the

planetary gears

22, 23, 24 is not required, and accordingly, the outer shape in the radial direction can be reduced in size.

[ fifth embodiment, sixth embodiment, seventh embodiment, eighth embodiment ]

In the torque vector distribution device TV shown in fig. 5, 6, 7, and 8, the differential mechanism 2 includes: three sets of planetary gears of a first planetary gear 22, a second planetary gear 23, and a third planetary gear 24; three sun gears, a first sun gear 25, a second sun gear 26, and a third sun gear 27; and a wheel carriage 28.

The third sun gear 27 is coupled to the differential ring gear 43 (or 51, 62). The third sun gear 27 rotates integrally with the differential ring gear 43 (or 51, 62). The first sun gear 25 is coupled to the first drive shaft 3. The first sun gear 25 rotates integrally with the first drive shaft 3. The second sun gear 26 is coupled to the second drive shaft 4. The second sun gear 26 rotates integrally with the second drive shaft 4.

Therefore, the third sun gear 27 serves as the power input element 17 of the differential mechanism 2, the first sun gear 25 serves as the first power output element 18 of the differential mechanism 2, and the carrier 28 serves as the first differential reaction element 19 of the differential mechanism 2, thereby constituting the first power planetary gear mechanism 15. The third sun gear 27 serves as the power input element 17 of the differential mechanism 2, the second sun gear 26 serves as the second power output element 20 of the differential mechanism 2, and the carrier 28 serves as the second differential reaction element 21 of the differential mechanism 2, thereby constituting the second power planetary gear mechanism 16.

The reversing mechanism 6 has: three sets of planetary gears of a first planetary gear 22, a second planetary gear 23, and a third planetary gear 24; three sun gears, a first sun gear 25, a second sun gear 26, and a third sun gear 27; and a wheel carriage 28. The reduction planetary gear mechanism 71 is provided coaxially with the reversing mechanism 6, the first drive shaft 3, and the second drive shaft 4.

The reduction planetary gear mechanism 71 is constituted by a single-row star-shaped planetary gear mechanism. The reduction planetary gear mechanism 71 has a sun gear 71a, a ring gear 71b, and a carrier 71 c. The sun gear 71a is coupled to a control torque output shaft 5a of the actuator 5. The sun gear 71a rotates integrally with the control torque output shaft 5 a. The ring gear 71b is formed in an inner peripheral portion of the differential case 14 to which the differential ring gear 43 (or 51, 62) is coupled. Alternatively, the ring gear 71b is coupled to the differential case 14. The ring gear 71b rotates integrally with the differential case 14. The carrier 71c supports the planetary gears 71d of the reduction planetary gear mechanism 71 so as to be rotatable and revolvable. The carrier 71c rotates integrally with the carrier 28. Therefore, the reduction planetary gear mechanism 71 amplifies the control torque output by the actuator 5 between the actuator 5 and the carrier 28 and transmits the amplified torque to the carrier 28.

The sun gear 71a of the reduction planetary gear mechanism 71 corresponds to the fourth sun gear of the reversing mechanism 6. Therefore, the reduction planetary gear mechanism 71 is constituted by the fourth sun gear 71a, the ring gear 71b, and the carrier 71 c. Therefore, the fourth sun gear 71a serves as the control input element 31, and the first sun gear 25 serves as the first gear 33 and the first control output element 32, thereby compositely constituting the first control planetary gear mechanism 29. The fourth sun gear 71a serves as the control input element 31, and the second sun gear 26 serves as the second gear 35 and the second control output element 34, thereby compositely configuring the second control planetary gear mechanism 30.

The planetary gear 71d of the reduction planetary gear mechanism 71, which meshes with the fourth sun gear 71a and the ring gear 71b, corresponds to the fourth planetary gear of the reversing mechanism 6. Therefore, the reduction planetary gear mechanism 71 has the fourth planetary gears 71d that mesh with the fourth sun gear 71a and the ring gear 71b at the same time. The fourth planetary gear 71d of the reduction planetary gear mechanism 71 is arranged coaxially with the first planetary gear 22, the second planetary gear 23, and the third planetary gear 24, and is arranged to be rotatable relative to the first planetary gear 22, the second planetary gear 23, and the third planetary gear 24. The carrier 71c of the reduction planetary gear mechanism 71 also serves as the carrier 28. That is, the carrier 28 holds the fourth planetary gears 71d of the reduction planetary gear mechanism 71 rotatably and revolvably together with the first planetary gears 22, the second planetary gears 23, and the third planetary gears 24, respectively.

In the above-described reversing mechanism 6, the carrier 28 is coupled to the control torque output shaft 5a of the actuator 5 via the reduction planetary gear mechanism 71. The first sun gear 25 is coupled to the first power output element 18 of the differential mechanism 2, i.e., the first driveshaft 3. The first sun gear 25 and the first planetary gears 22 mesh with each other. The second sun gear 26 is coupled to the second power output element 20 of the differential mechanism 2, i.e., the second drive shaft 4. The second sun gear 26 and the second planetary gears 23 mesh with each other.

Therefore, the carrier 28 serves as the control input element 31, and the first sun gear 25 serves as the first control output element 32 as the first gear 33, thereby constituting the first control planetary gear mechanism 29. The carrier 28 serves as a control input element 31, and the second sun gear 26 serves as a second control output element 34 as a second gear 35, thereby constituting a second control planetary gear mechanism 30.

In the examples shown in fig. 5, 6, 7, 8, the gear ratio of the first gear train 72 including the first planetary gears 22 and the first gear 33 (i.e., the first sun gear 25) and the gear ratio of the second gear train 73 including the second planetary gears 23 and the second gear 35 (i.e., the second sun gear 26) are different from each other. Specifically, the gear ratios of the gear pairs of the first planetary gears 22 and the first sun gear 25 in the first gear train 72 and the gear ratios of the gear pairs of the second planetary gears 23 and the second sun gear 26 in the second gear train 73 are different from each other.

More specifically, the number of teeth of the first sun gear 25, the number of teeth of the second sun gear 26, and the number of teeth of the third sun gear 27 are all equal. The number of teeth of the first planetary gear 22, the number of teeth of the second planetary gear 23, and the number of teeth of the third planetary gear 24 are each less than the number of teeth of each sun gear 25, 26, 27. Also, the number of teeth of the first planetary gears 22 is greater than that of the third planetary gears 24, and the number of teeth of the second planetary gears 23 is less than that of the third planetary gears 24.

For example, in the example shown in fig. 5, the number of teeth of each sun gear 25, 26, 27 is "40", the number of teeth of the first planetary gear 22 is "21", the number of teeth of the second planetary gear 23 is "19", and the number of teeth of the third planetary gear 24 is "20". In the example shown in fig. 5, the number of teeth of the sun gear 71a, the number of teeth of the ring gear 71b, and the number of teeth of the planet gears 71d are "40", "80", and "20", respectively, in the reduction planetary gear mechanism 71. In this case, the reduction ratio R is "R ± 60". By providing the reduction planetary gear mechanism 71, a larger reduction ratio can be obtained as compared with the above-described examples shown in fig. 1 and 2.

In the example shown in fig. 6 and 7, the number of teeth of the sun gear 71a, the number of teeth of the ring gear 71b, and the number of teeth of the planet gears 71d in the reduction planetary gear mechanism 71 are "30", respectively, "90", and "30", respectively. In this case, the reduction ratio R is "R ± 80". By providing the reduction planetary gear mechanism 71, a larger reduction ratio can be obtained as compared with the example shown in fig. 1 and 2 and the example shown in fig. 5 described above.

In the example shown in fig. 8, the number of teeth of the sun gear 71a, the number of teeth of the ring gear 71b, and the number of teeth of the planet gears 71d are "25", "60", and "20", respectively, in the reduction planetary gear mechanism 71. In this case, the reduction ratio R is "R ═ 72". By providing the reduction planetary gear mechanism 71, a larger reduction ratio can be obtained as compared with the example shown in fig. 1 and 2 and the example shown in fig. 5 described above.

In the above-described examples shown in fig. 5, 6, 7, and 8, the reduction planetary gear mechanism 71 is disposed coaxially with the first drive shaft 3 and the second drive shaft 4. Specifically, the first drive shaft 3, the second drive shaft 4, the reversing mechanism 6, and the reduction planetary gear mechanism 71 are all disposed on the same rotation axis AL. Therefore, even if the reduction planetary gear mechanism 71 is added, the structure can be simplified by using the bearing as well. Therefore, the reduction planetary gear mechanism 71 can be easily provided.

In the example shown in fig. 8, an electric motor 8 is provided as a power source. In the example shown in fig. 8, the electric motor 8 is disposed coaxially with the first drive shaft 3 and the second drive shaft 4. Specifically, the first drive shaft 3, the second drive shaft 4, the reversing mechanism 6, and the electric motor 8 are all disposed on the same rotation axis AL. Further, a speed reduction mechanism 74 is provided for amplifying the power torque output from the electric motor 8. In the example shown in fig. 8, the speed reduction mechanism 74 is constituted by a compound planetary gear mechanism in which two sets of planetary gear mechanisms are combined.

The speed reduction mechanism (i.e., compound planetary gear mechanism) 74 has a first sun gear 74a, a second sun gear 74b, a ring gear 74c, a first carrier 74d, a second carrier 74e, first planetary gears 74f, and second planetary gears 74 g. The first sun gear 74a and the second sun gear 74b are coaxially arranged in series and rotate integrally. The first planetary gear 74f meshes with the first sun gear 74 a. The first planetary gears 74f are also meshed with the ring gear 74c of the internal gear. The second planetary gear 74g meshes with the second sun gear 74 b. The second planetary gears 74g are also meshed with the ring gear 74 c. The first carrier 74d holds the first planetary gear 74f so as to be rotatable. The second carrier 74e holds the second planetary gear 74g so as to be rotatable and revolvable around the second sun gear 74 b. The first carrier 74d and the second carrier 74e are coaxially arranged in series. The second carrier 74e and the first carrier 74d rotate relative to each other.

The first sun gear 74a and the second sun gear 74b are coupled to the power torque output shaft 8a of the electric motor 8 as an input member 75. The first carrier 74d is non-rotatably fixed to the housing 7. The second carrier 74e is coupled to the differential case 14 and the third sun gear 27 of the differential mechanism 2. Therefore, the reduction mechanism 74 reduces the rotation speed of the second carrier 74e and the third sun gear 27 of the differential mechanism 2, i.e., the power input element 17 of the differential mechanism 2, relative to the input rotation speed of the first sun gear 74a and the second sun gear 74b, i.e., the input member 75. Therefore, the speed reduction mechanism 74 amplifies the power torque generated by the power source and transmits the amplified power torque to the power input element 17 of the differential mechanism 2.

As described above, in the example shown in fig. 8, the electric motor 8, i.e., the power source and reduction mechanism 74, is disposed coaxially with the first drive shaft 3 and the second drive shaft 4. Specifically, the first drive shaft 3, the second drive shaft 4, the reversing mechanism 6, the electric motor 8, and the speed reduction mechanism 74 are all disposed on the same rotation axis AL. Therefore, the main components of the torque vector distribution device TV shown in fig. 8 have a so-called single-shaft structure. Therefore, the torque vector distribution device TV can be reduced in size while suppressing the radial increase in size of the torque vector distribution device TV. Further, as shown in fig. 8, a cylindrical torque vector distribution device TV with a simple appearance can be configured. As a result, the torque vector distribution device TV can be easily mounted on the vehicle in a compact and simplified manner.

In the torque vector distribution devices TV of the first embodiment (fig. 1), the second embodiment (fig. 2), the third embodiment (fig. 3), the fourth embodiment (fig. 4), the fifth embodiment (fig. 5), the sixth embodiment (fig. 6), the seventh embodiment (fig. 7), and the eighth embodiment (fig. 8), the differential mechanism 2 and the reversing mechanism 6 are configured by sharing the first planetary gear 22, the second planetary gear 23, and the third planetary gear 24. The first planetary gear 22, the second planetary gear 23, and the third planetary gear 24 are coaxially arranged in series. The first planetary gear 22, the second planetary gear 23, and the third planetary gear 24 are each held by one carrier 28 so as to be rotatable and revolvable. The first planetary gears 22, the second planetary gears 23, and the third planetary gears 24 rotate integrally in the rotation direction. The third planetary gears 24 are engaged with the third sun gear 27 or the third ring gear 65 serving as the power input element 17. That is, the third planetary gears 24 are transmitted with the power torque from the power input member 17.

[ ninth embodiment ]

In the torque vector distribution device TV shown in fig. 9, the differential mechanism 2 includes: four sets of first, second, third, and fourth

planetary gears

81, 82, 83, and 84; four gear rings of a first gear ring 85, a second gear ring 86, a third gear ring 87, and a fourth gear ring 88; and a wheel carriage 89.

The first planetary gear 81, the second planetary gear 82, the third planetary gear 83, and the fourth planetary gear 84 are coaxially arranged in series. The first planetary gear 81, the second planetary gear 82, the third planetary gear 83, and the fourth planetary gear 84 are each held by a carrier 89 so as to be rotatable and revolvable. The first planetary gears 81 and the third planetary gears 83 rotate integrally in the rotation direction. The second planetary gears 82 and the fourth planetary gears 84 rotate integrally in the rotation direction. The first and third

planetary gears

81 and 83 and the second and fourth

planetary gears

82 and 84 are rotatable relative to each other.

The first ring gear 85, the second ring gear 86, the third ring gear 87, and the fourth ring gear 88 are coaxially arranged in series. The first ring gear 85 is an internal gear, and meshes with the first planetary gears 81. The second ring gear 86 is an internal gear, and meshes with the second planetary gears 82. The third ring gear 87 is an internal gear, and meshes with the third planetary gears 83. The fourth ring gear 88 is an internal gear, and meshes with the fourth planetary gears 84. The third ring gear 87 rotates integrally with the fourth ring gear 88. The first and second gear rings 85, 86 and the third and fourth gear rings 87, 88 are rotatable relative to each other.

The third ring gear 87 and the fourth ring gear 88 are both linked to the differential ring gear 62. The third ring gear 87 and the fourth ring gear 88 rotate integrally with the differential ring gear 62. The first ring gear 85 is coupled to the first drive shaft 3. The first ring gear 85 rotates integrally with the first drive shaft 3. The second ring gear 86 is coupled to the second drive shaft 4. The second ring gear 86 rotates integrally with the second drive shaft 4.

Therefore, the third ring gear 87 serves as the power input element 17 of the differential mechanism 2, the first ring gear 85 serves as the first power output element 18 of the differential mechanism 2, and the carrier 89 serves as the first differential reaction element 19 of the differential mechanism 2, thereby constituting the first power planetary gear mechanism 15. The fourth ring gear 88 serves as the power input element 17 of the differential mechanism 2, the second ring gear 86 serves as the second power output element 20 of the differential mechanism 2, and the carrier 89 serves as the second differential reaction element 21 of the differential mechanism 2, thereby constituting the second power planetary gear mechanism 16.

The reversing mechanism 6 has: four sets of first, second, third, and fourth

planetary gears

81, 82, 83, and 84; four gear rings of a first gear ring 85, a second gear ring 86, a third gear ring 87, and a fourth gear ring 88; and a wheel carriage 89. The carrier 89 is coupled to the control torque output shaft 5a of the actuator 5. The first ring gear 85 is coupled to the first power output element 18 of the differential mechanism 2, i.e., the first driveshaft 3. The first ring gear 85 and the first planetary gears 81 mesh with each other. The second ring gear 86 is coupled to the second power output element 20 of the differential mechanism 2, i.e., the second driveshaft 4. The second ring gear 86 and the second planetary gears 82 mesh with each other.

Therefore, the carrier 89 serves as the control input element 31, and the first ring gear 85 serves as the first gear 33 and the first control output element 32, thereby constituting the first control planetary gear mechanism 29. The carrier 89 serves as the control input element 31, and the second ring gear 86 serves as the second gear 35 and the second control output element 34, thereby constituting the second control planetary gear mechanism 30.

In the example shown in fig. 9, the gear ratio of the first gear train 90 including the first planetary gears 81 and the first gear 33 (i.e., the first ring gear 85) and the gear ratio of the second gear train 91 including the second planetary gears 82 and the second gear 35 (i.e., the second ring gear 86) are different from each other. Specifically, the gear ratios of the gear pairs of the first planetary gears 81, the third planetary gears 83, and the first ring gear 85 in the first gear train 90 and the gear ratios of the gear pairs of the second planetary gears 82, the fourth planetary gears 84, and the second ring gear 86 in the second gear train 91 are different from each other.

More specifically, the number of teeth of the first planetary gear 81 and the number of teeth of the second planetary gear 82 are equal to the number of teeth of the third planetary gear 83 and the number of teeth of the fourth planetary gear 84. The number of teeth of the first ring gear 85, the number of teeth of the second ring gear 86, the number of teeth of the third ring gear 87, and the number of teeth of the fourth ring gear 88 are each greater than the number of teeth of each of the pinion gears 81, 82, 83, 84. Further, the number of teeth of the first ring gear 85 is equal to that of the second ring gear 86. Also, the third ring gear 87 has fewer teeth than the first ring gear 85 and the second ring gear 86, and the fourth ring gear 88 has more teeth than the first ring gear 85 and the second ring gear 86.

For example, in the example shown in fig. 9, the number of teeth of each of the

planetary gears

81, 82, 83, 84 is "17", the number of teeth of the first ring gear 85 and the second ring gear 86 is "60", the number of teeth of the third ring gear 87 is "59", and the number of teeth of the fourth ring gear 88 is "61". In this case, the reduction ratio R is "R ± 60". By providing the four ring gears 85, 86, 87, 88 and the four sets of

planetary gears

81, 82, 83, 84 meshing with the respective ring gears 85, 86, 87, 88 as described above, a larger reduction ratio can be obtained as compared with the example shown in fig. 1 and 2 described above, for example.

In the torque vector distribution device TV of the ninth embodiment (fig. 9) described above, the differential mechanism 2 and the reversing mechanism 6 are configured by sharing the first planetary gear 81, the second planetary gear 82, the third planetary gear 83, and the fourth planetary gear 84. The first planetary gear 81, the second planetary gear 82, the third planetary gear 83, and the fourth planetary gear 84 are coaxially arranged in series. The first planetary gear 81, the second planetary gear 82, the third planetary gear 83, and the fourth planetary gear 84 are each held by one carrier 89 so as to be rotatable and revolvable. The first planetary gears 81 and the third planetary gears 83 rotate integrally in the rotation direction. Further, the second planetary gear 82 and the fourth planetary gear 84 rotate integrally in the rotation direction. The first and third

planetary gears

81 and 83 and the second and fourth

planetary gears

82 and 84 are rotatable relative to each other. The third planetary gears 83 and the fourth planetary gears 84 mesh with a third ring gear 87 and a fourth ring gear 88, respectively, which become the power input element 17. That is, the third planetary gears 83 and the fourth planetary gears 84 are transmitted with power torque from the power input element 17.

The order of arrangement of the first, second, third, and fourth

planetary gears

81, 82, 83, and 84, and the first, second, third, and fourth ring gears 85, 86, 87, and 88 is not limited to the order shown in fig. 9. For example, the first and third

planetary gears

81 and 83 and the first and third ring gears 85 and 87 may be arranged alternately with the second and fourth

planetary gears

82 and 84 and the second and fourth ring gears 86 and 88.

The differential mechanism 2 in each of the torque vector distribution devices TV of the first embodiment (fig. 1), the second embodiment (fig. 2), the third embodiment (fig. 3), the fourth embodiment (fig. 4), the fifth embodiment (fig. 5), the sixth embodiment (fig. 6), the seventh embodiment (fig. 7), the eighth embodiment (fig. 8), and the ninth embodiment (fig. 9) described above is connected to the power input element 17 through the input member 1 (or 41). The first power output element 18 is coupled to the first driveshaft 3. The second power output element 20 is coupled to the second drive shaft 4. In addition, the reversing mechanism 6 in each of the torque vector distribution devices TV of the first to ninth embodiments described above is coupled to the control input element 31 via the actuator 5. The first gear 33 forms the first control output element 32. The second gear 35 forms the second control output member 34. Also, the reversing mechanisms 6 are each configured to amplify and transmit the control torque input to the control input element 31 to the first drive shaft 3 and the second drive shaft 4.

Therefore, according to the torque vector distribution devices TV of the first to ninth embodiments described above, the control torque of the actuator 5 can be amplified and transmitted to the first drive shaft 3 and the second drive shaft 4 by the reversing mechanism 6. Therefore, the actuator 5 can be downsized in accordance with the amplification of the control torque by the deceleration function of the reversing mechanism 6. Further, the torque vector distribution device TV can be downsized in its outer shape. As a result, the downsized torque vector distribution device TV can be easily mounted on the vehicle.

[ tenth embodiment ]

Fig. 10 shows another example of the torque vector distribution device to which the present invention is applied. The torque vector distribution device TV according to the embodiment of the present invention includes, as main constituent elements, an input member 101, a differential mechanism 102, a first drive shaft 103, a second drive shaft 104, an actuator 105, and a reversing mechanism 106.

The input member 101 receives power torque output from the power source. In the example shown in fig. 10, an electric motor 108 incorporated in a casing 107 of the torque vector distribution device TV is provided as a power source. The electric motor 108 generates a driving torque or a regenerative torque as a motive torque, similarly to the electric motor 8 described above. The electric motor 108 is constituted by, for example, a permanent magnet type synchronous motor or an induction motor. The output shaft of the electric motor 108, i.e., the power torque output shaft 108a, is formed in a hollow shape. The motive torque output shaft 108a is coupled to a motive power input element 111 of the differential mechanism 102 described later, and transmits motive torque to the motive power input element 111. At the same time, the power torque output shaft 108a forms the input member 101. Therefore, the input member 101 has a hollow power torque output shaft 108a that transmits power torque to the differential mechanism 102 side.

The differential mechanism 102 is constituted by a first power planetary gear mechanism 109 and a second power planetary gear mechanism 110. The first power planetary gear mechanism 109 and the second power planetary gear mechanism 110 are disposed coaxially and in a left-right opposed manner. Specifically, the first and

second drive shafts

103 and 104 and the first and second power planetary gear mechanisms 109 and 110 are disposed on the same rotation axis AL.

The first power planetary gear mechanism 109 has a power input element 111, a first power output element 112, and a first differential reaction element 113. The power input element 111 is transmitted with power torque from the input member 101. The first power output element 112 outputs power torque to the first drive shaft 103. Control torque of an actuator 105, which will be described later, is transmitted to the first differential reaction element 113 as a reaction force to the power torque transmitted from the power input element 111 to the first power output element 112. On the other hand, the second power planetary gear mechanism 110 has a power input element 111, a second power output element 114, and a second differential reaction element 115. The power input element 111 shares the same function as the first power planetary gear mechanism 109 described above. The second power output member 114 outputs power torque to the second drive shaft 104. Control torque of an actuator 105, which will be described later, is transmitted to the second differential reaction element 115 as a reaction force to the motive torque transmitted from the power input element 111 to the second motive power output element 114. In the example shown in fig. 10, the first differential reaction element 113 and the second differential reaction element 115 are coupled via a later-described reversing mechanism 106.

The first power planetary gear mechanism 109 and the second power planetary gear mechanism 110 are each constituted by a compound planetary gear mechanism in which two sets of planetary gear mechanisms are combined.

The first power planetary gear mechanism 109 has a first sun gear 109a, a second sun gear 109b, a carrier 109c, first planetary gears 109d, and second planetary gears 109 e. The first sun gear 109a and the second sun gear 109b are coaxially arranged in series. Further, the first sun gear 109a and the second sun gear 109b rotate relative to each other. The first planetary gears 109d are meshed with the first sun gear 109 a. The second planetary gears 109e are meshed with the second sun gear 109 b. The carrier 109c holds the first planetary gear 109d and the second planetary gear 109e to be rotatable and revolvable around the first sun gear 109a and the second sun gear 109b, respectively. The first planetary gear 109d and the second planetary gear 109e rotate integrally in the rotation direction. The first power planetary gear mechanism 109 is disposed in a hollow portion of the power torque output shaft 108 a.

The second power planetary gear mechanism 110 has a first sun gear 110a, a second sun gear 110b, a carrier 110c, first planetary gears 110d, and second planetary gears 110 e. The first sun gear 110a and the second sun gear 110b are coaxially arranged in series. In addition, the first sun gear 110a and the second sun gear 110b rotate relative to each other. The first planetary gears 110d are engaged with the first sun gear 110 a. The second planetary gears 110e are engaged with the second sun gear 110 b. The carrier 110c holds the first planetary gear 110d and the second planetary gear 110e to be rotatable and revolvable around the first sun gear 110a and the second sun gear 110b, respectively. The first planetary gear 110d and the second planetary gear 110e rotate integrally in the rotation direction. The second power planetary gear mechanism 110 is disposed in a hollow portion of the power torque output shaft 108a and a hollow portion of the control torque output shaft 105a, which will be described later.

The carrier 109c and the carrier 110c are coupled to a power torque output shaft 108a of the electric motor 108 as the input member 101. Specifically, a power torque output shaft 108a of the electric motor 108 is connected to a carrier 109c of the first power planetary gear mechanism 109. The second sun gear 109b of the first power planetary gear mechanism 109 and the second sun gear 110b of the second power planetary gear mechanism 110 are each formed in a hollow shape. A coupling shaft 116 is disposed in the hollow portions of the second sun gear 109b and the second sun gear 110 b. The second sun gear 109b and the second sun gear 110b rotate relative to each other with the coupling shaft 116. The carrier 109c and the carrier 110c are connected to both end portions of the connecting shaft 116, respectively. The coupling shaft 116 rotates integrally with the carrier 109c and the carrier 110 c. Therefore, the power torque output shaft 108a rotates integrally with the carrier 109c and the carrier 110 c.

Therefore, the motive torque generated by the motive power source is transmitted to the carrier 109c via the input member 101, i.e., the motive torque output shaft 108 a. At the same time, the motive torque generated by the motive power source is transmitted to the carrier 110c via the motive torque output shaft 108a and the coupling shaft 116, which are the input member 101. Therefore, the carrier 109c and the carrier 110c become the power input element 111 of the differential mechanism 102.

The first sun gear 109a of the first power planetary gear mechanism 109 is coupled to the first drive shaft 103. The first sun gear 109a rotates integrally with the first drive shaft 103. Therefore, a part of the power torque transmitted to the differential mechanism 102 is output from the first sun gear 109a to the first drive shaft 103. Therefore, the first sun gear 109a serves as the first power output element 112 of the differential mechanism 102.

The first sun gear 110a of the second power planetary gear mechanism 110 is coupled to the second drive shaft 104. The first sun gear 110a rotates integrally with the second drive shaft 104. Therefore, a part of the power torque transmitted to the differential mechanism 102 is output from the first sun gear 110a to the second drive shaft 104. Therefore, the first sun gear 110a becomes the second power output element 114 of the differential mechanism 102.

The second sun gear 109b of the first power planetary gear mechanism 109 is coupled to a first sun gear 128 of the reversing mechanism 106, which will be described later. The second sun gear 109b rotates integrally with the first sun gear 128. A part of the control torque transmitted from the actuator 105 to the first sun gear 128 of the reversing mechanism 106 acts as a reaction force against the power torque transmitted from the power input element 111 to the first power output element 112. Therefore, the second sun gear 109b of the first power planetary gear mechanism 109 serves as the first differential reaction element 113 of the differential mechanism 102.

The second sun gear 110b of the second power planetary gear mechanism 110 is coupled to a second sun gear 129 of the reversing mechanism 106, which will be described later. The second sun gear 110b rotates integrally with the second sun gear 129. A part of the control torque transmitted from the actuator 105 to the second sun gear 129 of the reversing mechanism 106 acts as a reaction force against the power torque transmitted from the power input element 111 to the second power output element 114. Therefore, the second sun gear 110b of the second power planetary gear mechanism 110 serves as the second differential reaction element 115 of the differential mechanism 102.

In this way, in the differential mechanism 102, the carrier 109c serves as the power input element 111, the first sun gear 109a serves as the first power output element 112, and the second sun gear 109b serves as the first differential reaction element 113, thereby constituting the first power planetary gear mechanism 109. At the same time, the carrier 110c serves as the power input element 111, the first sun gear 110a serves as the second power output element 114, and the second sun gear 110b serves as the second differential reaction element 115, thereby constituting the second power planetary gear mechanism 110.

The first drive shaft 103 and the second drive shaft 104 are coaxially disposed to face left and right. Further, the first drive shaft 103 and the second drive shaft 104 are disposed coaxially with the first power planetary gear mechanism 109 and the second power planetary gear mechanism 110. Specifically, the first and

second drive shafts

103 and 104 and the first and second power planetary gear mechanisms 109 and 110 are disposed on the same rotation axis AL. The first drive shaft 103 and the second drive shaft 104 are rotatable relative to each other. The end of the first drive shaft 103 on the protruding side (the right side in fig. 10) is rotatably supported by the housing 107. Similarly, the end of the second drive shaft 104 on the protruding side (left side in fig. 10) is rotatably supported by the housing 107. For example, when the torque vector distribution device TV according to the embodiment of the present invention is mounted on a vehicle, drive wheels (not shown) are mounted on the first drive shaft 103 and the second drive shaft 104, respectively.

The first driveshaft 103 and the second driveshaft 104 are coupled to a first power output element 112 and a second power output element 114, respectively, of the differential mechanism 102. Therefore, the first drive shaft 103 and the second drive shaft 104 are differentially rotated by the action of the differential mechanism 102. For example, when a vehicle mounted with the torque vector distribution device TV according to the embodiment of the present invention performs turning, the differential mechanism 102 functions as a differential device of the vehicle, and the first drive shaft 103 and the second drive shaft 104 perform differential rotation according to a difference in rotation speed between the inner wheel and the outer wheel. When the control torque of the actuator 105 is changed to control the torque distribution to the left and right drive wheels, that is, when the torque vector distribution is performed, the first drive shaft 103 and the second drive shaft 104 perform differential rotation.

The actuator 105 gives the torque generated by the actuator 105 to the differential mechanism 102 as a control torque. The differential mechanism 102 differentially rotates the first drive shaft 103 and the second drive shaft 104 due to the first differential reaction element 113 and the second differential reaction element 115, to which control torques are applied to the differential mechanism 102. As the actuator 105, for example, an electric motor or a brake mechanism can be used. The electric motor outputs, as control torque, drive torque that drives the first differential reaction element 113 and the second differential reaction element 115. Alternatively, regenerative torque that brakes the first differential reaction element 113 and the second differential reaction element 115 is output as control torque. The brake mechanism outputs, as a control torque, a braking torque that brakes the first differential reaction element 113 and the second differential reaction element 115. For example, an excitation type electromagnetic brake that brakes a predetermined rotating member by magnetic attraction force generated by energization, an electric brake that generates friction braking force by using a feed screw mechanism driven by an electric motor, or the like may be used.

The actuator 105 has a control torque output shaft 105a that outputs the drive torque, the regenerative torque, or the brake torque as the control torque. In the example shown in fig. 10, an electric motor that outputs a drive torque or a regenerative torque as a control torque is used. Therefore, the rotor shaft of the electric motor becomes the control torque output shaft 105 a. The control torque output shaft 105a is coupled to a carrier shaft 132a of a carrier 132 in the reversing mechanism 106 described later. Further, the control torque output shaft 105a is formed in a hollow shape. A second power planetary gear mechanism 110 of the reversing mechanism 106 and the differential mechanism 102 is disposed in a hollow portion of the control torque output shaft 105 a.

As described above, in the torque vector distribution device TV according to the embodiment of the present invention, an electric motor or a brake mechanism may be used as the actuator 105. By controlling the electric motor to change the control torque, the differential rotation between the first drive shaft 103 and the second drive shaft 104 can be controlled. Alternatively, the differential rotation between the first drive shaft 103 and the second drive shaft 104 can be controlled by changing the control torque by controlling the brake mechanism. Further, the differential rotation between the first drive shaft 103 and the second drive shaft 104 can be restricted by the regenerative torque of the electric motor or the braking torque of the brake mechanism (differential lock).

The reversing mechanism 106 is disposed coaxially with the first drive shaft 103 and the second drive shaft 104. In the example shown in fig. 10, the reversing mechanism 106 is disposed in a hollow portion of a power torque output shaft 108a, which is an output shaft of the electric motor 108. When the first drive shaft 103 and the second drive shaft 104 rotate differentially, the reverse mechanism 106 rotates the first drive shaft 103 and the second drive shaft 104 in opposite directions to each other. The reversing mechanism 106 is constituted by a first control planetary gear mechanism 117 and a second control planetary gear mechanism 118. The first control planetary gear mechanism 117 and the second control planetary gear mechanism 118 are each disposed coaxially with the first drive shaft 103 and the second drive shaft 104. Specifically, the first and

second drive shafts

103 and 104 and the first and second control

planetary gear mechanisms

117 and 118 are all arranged on the same rotation axis AL. The first control planetary gear mechanism 117 transmits the control torque output by the actuator 105 to the first differential reaction element 113 of the differential mechanism 102. The second control planetary gear mechanism 118 transmits the control torque output by the actuator 105 to the second differential reaction element 115 of the differential mechanism 102.

The first control planetary gear mechanism 117 has a control input member 119, a first control output member 120, first planetary gears 121, and first gears 122. The control input element 119 is input with a control torque from the actuator 105. The first control output element 120 outputs a control torque to the first differential reaction element 113 of the differential mechanism 102 and the first driveshaft 103. The first planetary gears 121 are supplied control torque from the control input member 119. The first gear 122 meshes with the first planetary gears 121, forming the control input member 119 or the first control output member 120. On the other hand, the second control planetary gear mechanism 118 has a control input member 119, a second control output member 123, second planetary gears 124, and second gears 125. The control input element 119 is shared with the first control planetary gear mechanism 117 described above. The second control output element 123 outputs a control torque to the second differential reaction element 115 of the differential mechanism 102 and the second drive shaft 104. The second planetary gears 124 are transmitted control torque from the control input member 119. The second gear 125 meshes with the second planetary gear 124, forming the control input member 119 or the second control output member 123.

The reversing mechanism 106 includes: four sets of first, second, third and fourth planet gears 121, 124, 126 and 127; four sun gears, a first sun gear 128, a second sun gear 129, a third sun gear 130, and a fourth sun gear 131; and a wheel carriage 132.

The first planetary gear 121, the second planetary gear 124, the third planetary gear 126, and the fourth planetary gear 127 are coaxially arranged in series. The first planetary gear 121, the second planetary gear 124, the third planetary gear 126, and the fourth planetary gear 127 are each held by a carrier 132 so as to be rotatable and revolvable. The first planetary gears 121 and the third planetary gears 126 rotate integrally in the rotation direction. The second planetary gear 124 and the fourth planetary gear 127 rotate integrally in the rotation direction. The first and third

planetary gears

121 and 126 and the second and fourth

planetary gears

124 and 127 rotate relative to each other.

The first sun gear 128, the second sun gear 129, the third sun gear 130, and the fourth sun gear 131 are coaxially arranged in series. The first sun gear 128, the second sun gear 129, the third sun gear 130, and the fourth sun gear 131 are engaged with the first planetary gears 121, the second planetary gears 124, the third planetary gears 126, and the fourth planetary gears 127, respectively. The first sun gear 128 is coupled to the first differential reaction element 113 (i.e., the second sun gear 109b) of the differential mechanism 102. The second sun gear 129 is coupled to the second differential reaction element 115 (i.e., the second sun gear 110b) of the differential mechanism 102. The third sun gear 130 is coupled to the fourth sun gear 131. The first and second sun gears 128 and 129 and the third and fourth sun gears 130 and 131 rotate relative to each other.

The carrier 132 is coupled to the control torque output shaft 105a of the actuator 105. The first sun gear 128 is coupled to the second sun gear 109b of the differential mechanism 102. That is, the first sun gear 128 is coupled to the first drive shaft 103 via the second sun gear 109b and the first power planetary gear mechanism 109. The first sun gear 128 and the first planetary gears 121 mesh with each other. The second sun gear 129 is coupled to the second sun gear 110b of the differential mechanism 102. That is, the second sun gear 129 is coupled to the second drive shaft 104 via the second sun gear 110b and the second power planetary gear mechanism 110. The second sun gear 129 and the second planetary gears 124 mesh with each other.

Therefore, the carrier 132 serves as the control input element 119, and the first sun gear 128 serves as the first control output element 120 and the first gear 122, thereby constituting the first control planetary gear mechanism 117. The carrier 132 serves as the control input element 119, and the second sun gear 129 serves as the second control output element 123 and the second gear 125, thereby constituting the second control planetary gear mechanism 118.

In the example shown in fig. 10, the gear ratio of the first gear train 133 including the first planetary gears 121 and the first gear 122 (i.e., the first sun gear 128) and the gear ratio of the second gear train 134 including the second planetary gears 124 and the second gear 125 (i.e., the second sun gear 129) are different from each other. Specifically, the gear ratios of the gear pairs of the first planetary gears 121 and the first sun gear 128 in the first gear train 133 and the gear ratios of the gear pairs of the second planetary gears 124 and the second sun gear 129 in the second gear train 134 are different from each other.

More specifically, the number of teeth of the first sun gear 128 and the number of teeth of the second sun gear 129 are equal to the number of teeth of the third sun gear 130 and the number of teeth of the fourth sun gear 131. The number of teeth of the first planetary gear 121, the number of teeth of the second planetary gear 124, the number of teeth of the third planetary gear 126, and the number of teeth of the fourth planetary gear 127 are all less than the number of teeth of each sun gear 128, 129, 130, 131. In addition, the number of teeth of the third planetary gear 126 is equal to the number of teeth of the fourth planetary gear 127. Also, the number of teeth of the first planetary gear 121 is greater than the number of teeth of the third planetary gear 126 and the fourth planetary gear 127, and the number of teeth of the second planetary gear 124 is less than the number of teeth of the third planetary gear 126 and the fourth planetary gear 127. For example, as indicated by the parenthesized numerical values in fig. 10, the number of teeth of each of the sun gears 128, 129, 130, 131 is "34", the number of teeth of the first planetary gear 121 is "19", the number of teeth of the second planetary gear 124 is "17", and the number of teeth of the third planetary gear 126 and the fourth planetary gear 127 is "18".

In this case, when the number of teeth of the first planetary gear 121 is set to z_P1Z is the number of teeth of the first sun gear 128_S1In time, the gear ratio u of the first gear train 133₁The method comprises the following steps:

u₁＝z_P1/z_S1。

Therefore, for example, as in the above example, the number of teeth z of the first planetary gear 121_P1Is "19", the number of teeth z of the first sun gear 128_S134, the gear ratio u of the first gear train 133₁The method comprises the following steps:

u₁≈0.56。

similarly, when the number of teeth of the second planetary gear 124 is z_P2Z represents the number of teeth of the second sun gear 129_S2While the gear of the second gear train 134 is transmittingDynamic ratio u₂The method comprises the following steps:

u₂＝z_P2/z_S2。

therefore, for example, as in the above example, the number of teeth z of the second planetary gear 124_P2Is "17", the number of teeth z of the second sun gear 129_S234, the gear ratio u of the second gear train 134₂The method comprises the following steps:

u₂＝0.50。

the number z of teeth of the first planetary gear 121_P1Number z of teeth with the second planetary gear 124_P2Are different from each other, whereby the gear ratio u of the first gear train 133₁Gear ratio u to the second gear train 134₂Are different from each other.

As described above, the gear ratio u of the first gear train 133 in the first control planetary gear mechanism 117₁With the gear ratio u of the second gear train 134 in the second control planetary gear 118₂Different from each other, therefore, in a state where the rotation speed of the first drive shaft 103 is equal to the rotation speed of the second drive shaft 104, when the first control planetary gear mechanism 117 and the second control planetary gear mechanism 118 transmit torque, respectively, the first gear train 133 in the first control planetary gear mechanism 117 and the second gear train 134 in the second control planetary gear mechanism 118 interfere with each other. In the example shown in fig. 10, the number z of teeth of the first planetary gears 121 in the first gear train 133 _P1(19) The number of teeth z of the third planetary gear 126 in the gear train including the third sun gear 130 and the third planetary gear 126_P3(18) One more tooth, whereby the first sun gear 128 in the first gear train 133 is intended to rotate one tooth faster than the third sun gear 130. On the other hand, the number z of teeth of the second planetary gears 124 in the second gear train 134_P2(17) Number z of teeth of the fourth planetary gear 127 in the gear train of the fourth sun gear 131 and the fourth planetary gear 127_P4(18) One tooth less, so that the second sun gear 129 in the second gear train 134 is intended to rotate one tooth slower than the fourth sun gear 131. Therefore, the first sun gear 128 and the second sun gear 129 tend to rotate relatively in opposite directions. In this case, the first planet meshed with the first sun gear 128The gear 121 rotates integrally with the third planetary gears 126. On the other hand, the second planetary gears 124 meshed with the second sun gear 129 rotate integrally with the fourth planetary gears 127. The third sun gear 130 meshed with the third planetary gears 126 rotates integrally with the fourth sun gear 131 meshed with the fourth planetary gears 127. Therefore, the first planetary gear 121 and the second planetary gear 124 rotate and revolve integrally, and do not rotate relative to each other in the rotation direction and the revolution direction. Therefore, torques in opposite directions to each other act on the meshing portion of the first gear train 133 and the meshing portion of the second gear train 134, so that the first gear train 133 and the second gear train 134 interfere with each other. As a result, the reversing mechanism 106 is substantially engaged and integrally rotated. Therefore, the first drive shaft 103 and the second drive shaft 104 rotate integrally without performing differential rotation.

In contrast, in a state where there is a difference in rotational speed between the rotational speed of the first drive shaft 103 and the rotational speed of the second drive shaft 104, the substantial engagement state of the reversing mechanism 106 due to the interference of the gears between the first gear train 133 and the second gear train 134 as described above is released, and the first control planetary gear mechanism 117 and the second control planetary gear mechanism 118 are respectively released in accordance with the gear ratio u of the first gear train 133₁And the gear ratio u of the second gear train 134₂To transmit torque. In the example shown in fig. 10, the first gear train 133 and the second gear train 134 perform differential rotation, and thus the substantial engagement state of the reversing mechanism 106 is released. In this case, as described above, the torques in the opposite directions to each other act on the meshing portion of the first gear train 133 and the meshing portion of the second gear train 134. Therefore, the first sun gear 128 and the second sun gear 129 rotate relatively in opposite directions to each other. That is, the first sun gear 128 and the second sun gear 129 rotate so that the second sun gear 129 rotates in reverse with respect to the first sun gear 128. As a result, the first drive shaft 103 and the second drive shaft 104 rotate so that one drive shaft 103 (or 104) rotates in reverse with respect to the other drive shaft 104 (or 103). That is, the first drive shaft 103 and the second drive shaft 104 perform differential rotation and rotate relatively in opposite directions to each other.

Also, the reversing mechanism 106 is configured to: a first reduction ratio representing the proportion of the rotational speed of the first control output member 120 relative to the rotational speed of the control input member 119 and a second reduction ratio representing the proportion of the rotational speed of the second control output member 123 relative to the rotational speed of the control input member 119 are both greater than "1". In the example shown in fig. 10, it is configured such that both a first reduction ratio between the carrier 132 and the first sun gear 128 and a second reduction ratio between the carrier 132 and the second sun gear 129 are larger than "1". Therefore, the first control planetary gear mechanism 117 and the second control planetary gear mechanism 118 form a reduction gear mechanism that reduces the output rotational speed of the first sun gear 128 and the second sun gear 129 relative to the input rotational speed of the carrier 132, respectively. Therefore, the first control planetary gear mechanism 117 and the second control planetary gear mechanism 118 amplify the control torque of the actuator 105 input to the carrier 132 and transmit the amplified control torque to the first drive shaft 103 side and the second drive shaft 104 side.

For example, as in the above example, the number of teeth z of the first planetary gear 121_P1Is "19", the number of teeth z of the first sun gear 128_S134', the number of teeth z of the second planetary gear 124_P2Is "17", the number of teeth z of the second sun gear 129 _S2Number of teeth z of the third planetary gear 126 "34_P3Is "18", and the number of teeth z of the third sun gear 130_S3Number of teeth z of the fourth planetary gear 127 "34_P4Is "18", and the number of teeth z of the fourth sun gear 131_S4In the case of "34", the first reduction gear ratio R of the first control planetary gear mechanism 117₁And a second reduction gear ratio R of the second control planetary gear mechanism 118₂Respectively become:

R₁＝1/{1－(z_S3/z_P3)×(z_P1/z_S1)}≈18；

R₂＝1/{1－(z_S4/z_P4)×(z_P2/z_S2)}≈－18。

Need to make sure thatIn the first control planetary gear mechanism 117, the rotational direction of the first differential reaction element 113 (i.e., the second sun gear 109b) of the differential mechanism 102 and the rotational direction of the first power output element 112 (i.e., the first sun gear 109a) of the differential mechanism 102 are the same rotational direction, and the control torque is transmitted between the first differential reaction element 113 and the first power output element 112. On the other hand, in the second control planetary gear mechanism 118, the rotation direction of the second power output element 114 (i.e., the first sun gear 110a) of the differential mechanism 102 is reversed with respect to the rotation direction of the second differential reaction element 115 (i.e., the second sun gear 110b) of the differential mechanism 102, and a control torque is transmitted between the second differential reaction element 115 and the second power output element 114. Therefore, if the rotation direction of the first power output element 112 in the first control planetary gear mechanism 117 is set to the positive rotation direction, the rotation direction of the second power output element 114 in the second control planetary gear mechanism 118 becomes the negative rotation direction or the reverse rotation direction. Therefore, in the description of the embodiment of the present invention, for convenience, the second reduction gear ratio R of the second control planetary gear mechanism 118 is set to be lower than that of the first control planetary gear mechanism ₂The sign of minus (-) is noted. In the example shown in fig. 10, the reduction ratio R between the actuator 105 and the first and

second drive shafts

103 and 104 in the reversing mechanism 106 is represented as "R ═ 18".

As described above, in the torque vector distribution device TV according to the embodiment of the present invention, the first control planetary gear mechanism 117 and the second control planetary gear mechanism 118 in the reversing mechanism 106 each form a reduction gear mechanism having a reduction ratio larger than "1". That is, the reversing mechanism 106 has a reversing function of relatively rotating the first drive shaft 103 and the second drive shaft 104 in opposite rotational directions to each other when the first drive shaft 103 and the second drive shaft 104 are differentially rotated, and also has a speed reducing function (torque amplifying function) of amplifying the control torque of the actuator 105. In the example shown in fig. 10, the torque amplification function is provided, which has a large reduction gear ratio of "18". Therefore, according to the torque vector distribution device TV of the embodiment of the present invention, the actuator 105 can be downsized in accordance with the enlargement of the control torque by the deceleration function of the reversing mechanism 106. Therefore, the torque vector distribution device TV can be miniaturized.

In the torque vector distribution device TV according to the embodiment of the present invention, the reversing mechanism 106 has a single-shaft structure. Therefore, the reversing mechanism 106 having both the reversing function and the decelerating function as described above can be easily configured without using a complicated structure. Further, by disposing the reversing mechanism 106 coaxially with the first drive shaft 103 and the second drive shaft 104, the torque vector distribution device TV can be prevented from being increased in size in the radial direction. Further, the actuator 105 can be downsized by the deceleration function of the reversing mechanism 106. Therefore, according to the torque vector distribution device TV of the embodiment of the present invention, the inversion mechanism 106 and the actuator 105 can be easily downsized, and further, the outer shape of the torque vector distribution device TV can be downsized. As a result, the downsized torque vector distribution device TV can be easily mounted on the vehicle.

In the torque vector distribution device TV according to the embodiment of the present invention, the power torque output shaft 108a of the electric motor 108 as the power source is formed in a hollow shape, and the control torque output shaft 105a of the actuator 105 is formed in a hollow shape. The differential mechanism 102 and the reversing mechanism 106 are disposed in a hollow portion of the power torque output shaft 108a and a hollow portion of the control torque output shaft 105 a. Therefore, as described above, the reversing mechanism 106 has a single-shaft structure, and the torque vector distribution device TV can be reduced in size while suppressing the radial increase in size of the torque vector distribution device TV. As shown in fig. 10, a cylindrical torque vector distribution device TV with a simple appearance can be configured. As a result, the torque vector distribution device TV can be easily mounted on the vehicle in a compact and simplified manner.

The order of arrangement of the first planetary gears 121, the second planetary gears 124, the third planetary gears 126, and the fourth planetary gears 127, and the first sun gear 128, the second sun gear 129, the third sun gear 130, and the fourth sun gear 131 is not limited to the order shown in fig. 10. For example, the first and third

planetary gears

121, 126 and the first and third sun gears 128, 130 may be disposed alternately with the second and fourth

planetary gears

124, 127 and the second and fourth sun gears 129, 131.

[ eleventh embodiment ]

In the torque vector distribution device TV shown in fig. 11, the differential mechanism 102 is constituted by a first power planetary gear mechanism 141 and a second power planetary gear mechanism 142. The first power planetary gear mechanism 141 and the second power planetary gear mechanism 142 are coaxially disposed so as to face left and right. Specifically, the first and

second drive shafts

103 and 104 and the first and second power planetary gear mechanisms 141 and 142 are disposed on the same rotation axis AL.

The first power planetary gear mechanism 141 and the second power planetary gear mechanism 142 are each constituted by a single-pinion type planetary gear mechanism.

The first power planetary gear mechanism 141 includes a sun gear 141a, a ring gear 141b, and a carrier 141 c. The sun gear 141a is coupled to a first sun gear 149 of the reversing mechanism 106 described later. The sun gear 141a rotates integrally with the first sun gear 149. The ring gear 141b is coupled to an output shaft of the power source, i.e., the power torque output shaft 108a of the electric motor 108. In other words, the ring gear 141b of the internal gear is formed on the inner periphery of the hollow portion of the power torque output shaft 108 a. The carrier 141c is coupled to the first drive shaft 103 via a first output torque reduction mechanism 143 described later. The first power planetary gear mechanism 141 is disposed in the hollow portion of the power torque output shaft 108 a.

The first output torque reduction mechanism 143 is constituted by a single-row star-shaped planetary gear mechanism. The first output torque reduction mechanism 143 amplifies and transmits the power torque output by the power source to the first drive shaft 103 between the carrier 141c and the first drive shaft 103.

The second power planetary gear mechanism 142 includes a sun gear 142a, a ring gear 142b, and a carrier 142 c. The sun gear 142a is coupled to a second sun gear 150 of the reversing mechanism 106 described later. The sun gear 142a rotates integrally with the second sun gear 150. The ring gear 142b is coupled to the power torque output shaft 108a of the electric motor 108 via a coupling mechanism 144. The coupling mechanism 144 includes a coupling shaft 144a, and a gear pair 144b and a gear pair 144c provided at both ends of the coupling shaft 144 a. The coupling mechanism 144 transmits the motive torque output by the motive power source between the motive torque output shaft 108a and the ring gear 142 b. The carrier 142c is coupled to the second drive shaft 104 via a second output torque reduction mechanism 145 described later. The second power planetary gear mechanism 142 is disposed in a hollow portion of the control torque output shaft 105 a.

The second output torque reduction mechanism 145 is constituted by a single-row star-shaped planetary gear mechanism. The second output torque reduction mechanism 145 amplifies and transmits the power torque output by the power source to the second drive shaft 104 between the carrier 142c and the second drive shaft 104.

The ring gear 141b of the first power planetary gear mechanism 141 is coupled to the power torque output shaft 108a of the electric motor 108. The motive torque generated by the motive power source is transmitted to the ring gear 141b via the input member 101, i.e., the motive torque output shaft 108 a. At the same time, the motive torque generated by the motive power source is transmitted to the ring gear 142b via the motive torque output shaft 108a and the coupling mechanism 144. Therefore, the ring gear 141b and the ring gear 142b become the power input element 111 of the differential mechanism 102.

The carrier 141c of the first power planetary gear mechanism 141 is coupled to the first drive shaft 103 via the first output torque reduction mechanism 143. A part of the power torque transmitted to the differential mechanism 102 is transmitted from the carrier 141c to the first output torque reduction mechanism 143, amplified by the first output torque reduction mechanism 143, and output to the first drive shaft 103. Therefore, the carrier 141c becomes the first power output element 112 of the differential mechanism 102.

The sun gear 141a of the first power planetary gear mechanism 141 is coupled to a first sun gear 149 of the reversing mechanism 106, which will be described later. A part of the control torque transmitted from the actuator 105 to the first sun gear 149 of the reversing mechanism 106 acts as a reaction force against the power torque transmitted from the power input element 111 to the first power output element 112. Therefore, the sun gear 141a serves as the first differential reaction element 113 of the differential mechanism 102.

The carrier 142c of the second power planetary gear mechanism 142 is coupled to the second drive shaft 104 via a second output torque reduction mechanism 145. A part of the power torque transmitted to the differential mechanism 102 is transmitted from the carrier 142c to the second output torque reduction mechanism 145, amplified by the second output torque reduction mechanism 145, and output to the second drive shaft 104. Therefore, the carrier 142c becomes the second power output element 114 of the differential mechanism 102.

The sun gear 142a of the second power planetary gear mechanism 142 is coupled to a second sun gear 150 of the reversing mechanism 106, which will be described later. A part of the control torque transmitted from the actuator 105 to the second sun gear 150 of the reversing mechanism 106 acts as a reaction force against the power torque transmitted from the power input element 111 to the second power output element 114. Therefore, the sun gear 142a serves as the second differential reaction element 115 of the differential mechanism 102.

The reversing mechanism 106 includes: three sets of first, second, and third planetary gears 146, 147, and 148; three sun gears, a first sun gear 149, a second sun gear 150, and a third sun gear 151; and a wheel carriage 152. The reversing mechanism 106 is disposed in a hollow portion of the power torque output shaft 108 a.

The first planetary gear 146, the second planetary gear 147, and the third planetary gear 148 are coaxially arranged in series. The first planetary gears 146, the second planetary gears 147, and the third planetary gears 148 rotate integrally in the rotation direction.

The first sun gear 149, the second sun gear 150, and the third sun gear 151 are coaxially arranged in series. The first sun gear 149 and the second sun gear 150 and the third sun gear 151 rotate relative to each other. The first sun gear 149, the second sun gear 150, and the third sun gear 151 are engaged with the first planetary gears 146, the second planetary gears 147, and the third planetary gears 148, respectively.

The carrier 152 holds the planetary gears 146, 147, and 148 so as to be rotatable and revolvable, respectively.

The carrier 152 is coupled to the control torque output shaft 105a of the actuator 105. The first sun gear 149 is coupled to the sun gear 141a, i.e., the first differential reaction element 113 of the differential mechanism 102. The first sun gear 149 and the first planetary gears 146 mesh with each other. The second sun gear 150 is coupled to the sun gear 142a, i.e., the second differential reaction element 115 of the differential mechanism 102. The second sun gear 150 and the second planetary gears 147 are engaged with each other.

Therefore, the carrier 152 serves as the control input element 119, and the first sun gear 149 serves as the first control output element 120 and the first gear 122, thereby constituting the first control planetary gear mechanism 117. The carrier 152 serves as the control input element 119, and the second sun gear 150 serves as the second control output element 123 and the second gear 125, thereby constituting the second control planetary gear mechanism 118.

In the example shown in fig. 11, the gear ratio of the first gear train 153 including the first planetary gears 146 and the first gear 122 (i.e., the first sun gear 149) and the gear ratio of the second gear train 154 including the second planetary gears 147 and the second gear 125 (i.e., the second sun gear 150) are different from each other. Specifically, the gear ratios of the gear pairs of the first planetary gears 146 and the first sun gear 149 in the first gear train 153 and the gear ratios of the gear pairs of the second planetary gears 147 and the second sun gear 150 in the second gear train 154 are different from each other.

More specifically, the number of teeth of the first sun gear 149 is equal to that of the second sun gear 150 and that of the third sun gear 151. The number of teeth of the first planetary gear 146 is greater than that of the third planetary gear 148, and the number of teeth of the second planetary gear 147 is less than that of the third planetary gear 148.

For example, in the example shown in fig. 11, the number of teeth of each of the sun gears 149, 150, and 151 is "24", the number of teeth of the first planetary gear 146 is "36", the number of teeth of the second planetary gear 147 is "18", and the number of teeth of the third planetary gear 148 is "24". In this case, the reduction ratio R becomes "R ═ 3". In the torque vector distribution device TV shown in fig. 11, the obtained reduction ratio is relatively small as compared with the example shown in fig. 10, for example. However, in the example shown in fig. 11, the load applied to the reversing mechanism 106 is reduced, and therefore the reversing mechanism 106 can be made smaller. Therefore, the torque vector distribution device TV can be downsized.

The order of arrangement of the first planetary gears 146, the second planetary gears 147, and the third planetary gears 148, and the first sun gear 149, the second sun gear 150, and the third sun gear 151 is not limited to the order shown in fig. 11. For example, the first planetary gear 146 and the first sun gear 149 may be disposed alternately with the second planetary gear 147 and the second sun gear 150.

[ twelfth embodiment ]

In the torque vector distribution device TV shown in fig. 12, the differential mechanism 102 is constituted by a first power planetary gear mechanism 161 and a second power planetary gear mechanism 162. The first power planetary gear mechanism 161 and the second power planetary gear mechanism 162 are coaxially disposed so as to face left and right. Specifically, the first and

second drive shafts

103 and 104 and the first and second power planetary gear mechanisms 161 and 162 are arranged on the same rotation axis AL.

The first power planetary gear mechanism 161 and the second power planetary gear mechanism 162 are each constituted by a single-pinion type planetary gear mechanism.

The first power planetary gear mechanism 161 includes a sun gear 161a, a ring gear 161b, and a carrier 161 c. The sun gear 161a is coupled to a first sun gear 172 of the reversing mechanism 106 described later. The sun gear 161a rotates integrally with the first sun gear 172. The ring gear 161b has an input gear 161d of an external gear formed on an outer peripheral portion thereof. The input gear 161d meshes with the counter gear 163. The counter gear 163 is rotatably supported by a counter gear shaft 163 a. Both ends of the counter gear shaft 163a are fixed to the housing 107. The counter gear 163 meshes with a first pinion gear 164 provided on a first power torque output shaft 108b described later, together with the input gear 161 d. Therefore, the ring gear 161b is coupled to the first motive torque output shaft 108b via a gear train 165 including an input gear 161d, a counter gear 163, and a first pinion 164. The carrier 161c is coupled to the first drive shaft 103.

The second power planetary gear mechanism 162 has a sun gear 162a, a ring gear 162b, and a carrier 162 c. The sun gear 162a is coupled to a second sun gear 173 of the reversing mechanism 106 described later. The sun gear 162a rotates integrally with the second sun gear 173. The ring gear 162b has an input gear 162d of an external gear formed on an outer peripheral portion thereof. The input gear 162d meshes with the counter gear 166. The counter gear 166 is rotatably supported by a counter gear shaft 166 a. Both ends of the counter gear shaft 166a are fixed to the housing 107. The counter gear 166 meshes with a second pinion gear 167 provided on a second power torque output shaft 108c described later, together with the input gear 162 d. Therefore, the ring gear 162b is linked to the second motive torque output shaft 108c via a gear train 168 including the input gear 162d, the counter gear 166, and the second pinion gear 167. The carrier 162c is coupled to the second drive shaft 104.

In the example shown in fig. 12, the electric motor 108 as the motive power source has a first motive torque output shaft 108b and a second motive torque output shaft 108c as the motive torque output shaft 108 a. The first motive torque output shaft 108b and the second motive torque output shaft 108c are arranged coaxially and in a left-right opposed manner. The first motive torque output shaft 108b protrudes toward the first drive shaft 103 (left side in fig. 12). A first pinion gear 164 is fitted to the protruding portion of the first power torque output shaft 108 b. The second motive torque output shaft 108c protrudes toward the second drive shaft 104 (right side in fig. 12). A second pinion gear 167 is fitted to the protruding portion of the second power torque output shaft 108 c.

The ring gear 161b of the first power planetary gear mechanism 161 is coupled to the first power torque output shaft 108b of the electric motor 108 via a gear train 165. The motive torque generated by the power source is transmitted to the ring gear 161b via the input member 101, i.e., the first motive torque output shaft 108b, and the gear train 165. The ring gear 162b of the second power planetary gear mechanism 162 is coupled to the second power torque output shaft 108c of the electric motor 108 via a gear train 168. Power torque generated by the power sources is transferred to the ring gear 162b via the input member 101, i.e., the second power torque output shaft 108c, and the gear train 168. Therefore, the ring gear 161b and the ring gear 162b become the power input element 111 of the differential mechanism 102.

The carrier 161c of the first power planetary gear mechanism 161 is coupled to the first drive shaft 103. A part of the power torque transmitted to the differential mechanism 102 is output from the carrier 161c to the first drive shaft 103. Therefore, the carrier 161c becomes the first power output element 112 of the differential mechanism 102.

The sun gear 161a of the first power planetary gear mechanism 161 is coupled to a first sun gear 172 of the reversing mechanism 106, which will be described later. A part of the control torque transmitted from the actuator 105 to the first sun gear 172 of the reversing mechanism 106 acts as a reaction force against the power torque transmitted from the power input element 111 to the first power output element 112. Therefore, the sun gear 161a serves as the first differential reaction element 113 of the differential mechanism 102.

The carrier 162c of the second power planetary gear mechanism 162 is coupled to the second drive shaft 104. A part of the power torque transmitted to the differential mechanism 102 is output from the carrier 162c to the second drive shaft 104. Therefore, the carrier 162c becomes the second power output element 114 of the differential mechanism 102.

The sun gear 162a of the second power planetary gear mechanism 162 is coupled to a second sun gear 173 of the reversing mechanism 106, which will be described later. A part of the control torque transmitted from the actuator 105 to the second sun gear 173 of the reverse mechanism 106 acts as a reaction force against the power torque transmitted from the power input element 111 to the second power output element 114. Therefore, the sun gear 162a serves as the second differential reaction element 115 of the differential mechanism 102.

The reversing mechanism 106 includes: three sets of first planetary gears 169, second planetary gears 170, and third planetary gears 171; three sun gears, a first sun gear 172, a second sun gear 173, and a third sun gear 174; and a wheel carriage 175.

The first planetary gear 169, the second planetary gear 170, and the third planetary gear 171 are coaxially arranged in series. The first planetary gears 169, the second planetary gears 170, and the third planetary gears 171 rotate integrally in the rotation direction.

The first sun gear 172, the second sun gear 173, and the third sun gear 174 are coaxially arranged in series. The first sun gear 172, the second sun gear 173 and the third sun gear 174 rotate relative to each other. The first sun gear 172, the second sun gear 173, and the third sun gear 174 are engaged with the first planetary gears 169, the second planetary gears 170, and the third planetary gears 171, respectively.

The carrier 175 holds the

planetary gears

169, 170, and 171 rotatably and revolvably. The reversing mechanism 106 and the actuator 105 are arranged together with the first and

second drive shafts

103 and 104 and the first and second power planetary gear mechanisms 161 and 162 on the same rotation axis AL. Further, the reversing mechanism 106 and the actuator 105 are disposed between the first power planetary gear mechanism 161 and the second power planetary gear mechanism 162 on the rotation axis AL.

The carrier 175 is coupled to the control torque output shaft 105a of the actuator 105. The first sun gear 172 is coupled to the sun gear 161a, i.e., the first differential reaction element 113 of the differential mechanism 102. The first sun gear 172 and the first planetary gears 169 mesh with each other. The second sun gear 173 is coupled to the sun gear 162a, that is, the second differential reaction element 115 of the differential mechanism 102. The second sun gear 173 and the second planetary gears 170 are engaged with each other.

Therefore, the carrier 175 serves as the control input element 119, and the first sun gear 172 serves as the first control output element 120 and the first gear 122, thereby constituting the first control planetary gear mechanism 117. The carrier 175 serves as the control input element 119, and the second sun gear 173 serves as the second control output element 123 and the second gear 125, thereby constituting the second control planetary gear mechanism 118.

In the example shown in fig. 12, the gear ratios of a first gear train 176 including the first planetary gears 169 and the first gear 122 (i.e., the first sun gear 172) and a second gear train 177 including the second planetary gears 170 and the second gear 125 (i.e., the second sun gear 173) are different from each other. Specifically, the gear ratios of the gear pairs of the first planetary gears 169 and the first sun gear 172 in the first gear train 176 and the gear ratios of the gear pairs of the second planetary gears 170 and the second sun gear 173 in the second gear train 177 are different from each other.

More specifically, the number of teeth of the first sun gear 172, the number of teeth of the second sun gear 173, and the number of teeth of the third sun gear 174 are all equal. The number of teeth of the first planetary gears 169 is less than that of the third planetary gears 171, and the number of teeth of the second planetary gears 170 is more than that of the third planetary gears 171.

For example, in the example shown in fig. 12, the number of teeth of each of the sun gears 172, 173, and 174 is "34", the number of teeth of the first planetary gear 169 is "17", the number of teeth of the second planetary gear 170 is "19", and the number of teeth of the third planetary gear 171 is "18". In this case, the reduction ratio R is "R ═ 18". A relatively large reduction ratio is obtained compared to the reduction ratio that can be achieved with a conventional general planetary gear mechanism, which is approximately 4 to 10 or so.

The order of arrangement of the first planetary gears 169, the second planetary gears 170, the third planetary gears 171, and the first sun gear 172, the second sun gear 173, and the third sun gear 174 is not limited to the order shown in fig. 12. For example, the first planetary gear 169 and the first sun gear 172 may be disposed alternately with the second planetary gear 170 and the second sun gear 173.

[ thirteenth embodiment ]

In the torque vector distribution device TV shown in fig. 13, the differential mechanism 102 is constituted by the first power planetary gear mechanism 109 and the second power planetary gear mechanism 110, as in the case of the example shown in fig. 10 described above. The first power planetary gear mechanism 109 and the second power planetary gear mechanism 110 are both disposed on the same rotation axis AL as the first drive shaft 103 and the second drive shaft 104.

The reversing mechanism 106 includes: four sets of first, second, third and fourth planet gears 181, 182, 183 and 184; four sun gears of a first sun gear 185, a second sun gear 186, a third sun gear 187, and a fourth sun gear 188; four gear rings of a first gear ring 189, a second gear ring 190, a third gear ring 191, and a fourth gear ring 192; and three wheel frames of a first wheel frame 193, a second wheel frame 194, and a third wheel frame 195. The reversing mechanism 106 is disposed in a hollow portion of the power torque output shaft 108 a.

The first planetary gear 181, the second planetary gear 182, the third planetary gear 183, and the fourth planetary gear 184 are coaxially arranged in series. The first and second

planetary gears

181 and 182 and the third and fourth

planetary gears

183 and 184 rotate relative to each other.

The first sun gear 185, the second sun gear 186, the third sun gear 187, and the fourth sun gear 188 are coaxially arranged in series. The first sun gear 185 rotates integrally with the third sun gear 187. The second sun gear 186 rotates integrally with the fourth sun gear 188. The first and third sun gears 185 and 187 and the second and fourth sun gears 186 and 188 rotate relative to each other. The first sun gear 185, the second sun gear 186, the third sun gear 187, and the fourth sun gear 188 mesh with the first planetary gear 181, the second planetary gear 182, the third planetary gear 183, and the fourth planetary gear 184, respectively.

The first ring gear 189, the second ring gear 190, the third ring gear 191, and the fourth ring gear 192 are coaxially arranged in series. The first and second ring gears 189 and 190 and the third and fourth ring gears 191 and 192 each rotate integrally. The first, second, third, and fourth ring gears 189, 190, 191, and 192 mesh with the first, second, third, and fourth

planetary gears

181, 182, 183, and 184, respectively.

First wheel frame 193, second wheel frame 194, and third wheel frame 195 are coaxially arranged in series. The first wheel frame 193, the second wheel frame 194 and the third wheel frame 195 rotate relative to each other. The first carrier 193 holds the first planetary gear 181 rotatably and revolvably. The second carrier 194 holds the second planetary gears 182 so as to be rotatable and revolvable. The third carrier 195 holds the third planetary gears 183 and the fourth planetary gears 184 rotatably and revolvably, respectively.

The ring gears 189, 190, 191, and 192 are coupled to the control torque output shaft 105a of the actuator 105. The first carrier 193 is coupled to the second sun gear 109b, i.e., the first differential reaction element 113 of the differential mechanism 102. The first sun gear 185 and the first ring gear 189 are meshed together with the first planetary gears 181. The second carrier 194 is coupled to the second sun gear 110b, that is, the second differential reaction force element 115 of the differential mechanism 102. The second planetary gears 182 are meshed with the second sun gear 186 and the first ring gear 189. The second sun gear 186 and the second ring gear 190 together mesh with the second planetary gears 182.

Therefore, the first ring gear 189 serves as the control input element 119 and the first gear 122, and the first carrier 193 serves as the first control output element 120, thereby constituting the first control planetary gear mechanism 117. The second ring gear 190 serves as the control input element 119 and the second gear 125, and the second carrier 194 serves as the second control output element 123, thereby constituting the second control planetary gear mechanism 118.

In the example shown in fig. 13, the gear ratio of the first gear train 196 including the first planetary gears 181, the first gear 122 (i.e., the first ring gear 189), and the first sun gear 185 and the gear ratio of the second gear train 197 including the second planetary gears 182, the second gear 125 (i.e., the second ring gear 190), and the second sun gear 186 are different from each other. Specifically, the gear ratios of the gear pairs of the first planetary gears 181, the first ring gear 189, and the first sun gear 185 in the first gear train 196 and the gear ratios of the gear pairs of the second planetary gears 182, the second ring gear 190, and the second sun gear 186 in the second gear train 197 are different from each other.

More specifically, the number of teeth of the first planetary gear 181 and the number of teeth of the second planetary gear 182 are equal to the number of teeth of the third planetary gear 183 and the number of teeth of the fourth planetary gear 184. The number of teeth of the third sun gear 187 is equal to that of the fourth sun gear 188. The number of teeth of the first sun gear 185 is smaller than those of the third sun gear 187 and the fourth sun gear 188. In addition, the number of teeth of the second sun gear 186 is greater than those of the third sun gear 187 and the fourth sun gear 188. The number of teeth of the third ring gear 191 is equal to that of the fourth ring gear 192. The first ring gear 189 has a larger number of teeth than the third ring gear 191 and the fourth ring gear 192. Further, the number of teeth of the second ring gear 190 is smaller than the number of teeth of the third ring gear 191 and the fourth ring gear 192.

For example, in the example shown in fig. 13, the number of teeth of the first sun gear 185 is "29", the number of teeth of the second sun gear 186 is "31", the number of teeth of the third sun gear 187 and the fourth sun gear 188 is "30", the number of teeth of the first ring gear 189 is "67", the number of teeth of the second ring gear 190 is "65", and the number of teeth of the third ring gear 191 and the fourth ring gear 192 is "66". In this case, the reduction ratio R is "R ═ 30". A relatively large reduction ratio is obtained compared to the reduction ratio that can be achieved with a conventional general planetary gear mechanism, which is approximately 4 to 10 or so.

The order of arrangement of the first planetary gears 181, the second planetary gears 182, the third planetary gears 183, and the fourth planetary gears 184, the first sun gear 185, the second sun gear 186, the third sun gear 187, and the fourth sun gear 188, the first ring gear 189, the second ring gear 190, the third ring gear 191, and the fourth ring gear 192 is not limited to the order shown in fig. 13. For example, the first and third

planetary gears

181 and 183, the first and third sun gears 185 and 187, the first and third ring gears 189 and 191, the second and fourth

planetary gears

182 and 184, the second and fourth sun gears 186 and 188, and the second and fourth ring gears 190 and 192 may be alternately arranged.

[ fourteenth embodiment ]

In the torque vector distribution device TV shown in fig. 14, the differential mechanism 102 is constituted by a first power planetary gear mechanism 201 and a second power planetary gear mechanism 202. The first power planetary gear mechanism 201 and the second power planetary gear mechanism 202 are disposed coaxially and in a left-right opposed manner. Specifically, the first and

second drive shafts

103 and 104 and the first and second power planetary gear mechanisms 201 and 202 are arranged on the same rotation axis AL.

The first power planetary gear mechanism 201 and the second power planetary gear mechanism 202 are each constituted by a compound planetary gear mechanism in which two sets of planetary gear mechanisms are combined.

The first power planetary gear mechanism 201 has a first ring gear 201a, a second ring gear 201b, a carrier 201c, first planetary gears 201d, and second planetary gears 201 e. The first ring gear 201a and the second ring gear 201b are coaxially arranged in series. Further, the first ring gear 201a and the second ring gear 201b rotate relative to each other. The first planetary gears 201d are meshed with the first ring gear 201 a. The second planetary gear 201e is meshed with the second ring gear 201 b. The carrier 201c holds the first planetary gear 201d and the second planetary gear 201e respectively to be rotatable and revolvable around the rotation axis AL. The first planetary gear 201d and the second planetary gear 201e rotate integrally in the rotation direction. The first power planetary gear mechanism 201 is disposed in a hollow portion of the power torque output shaft 108 a.

The second power planetary gear mechanism 202 has a first ring gear 202a, a second ring gear 202b, a carrier 202c, first planetary gears 202d, and second planetary gears 202 e. The first ring gear 202a and the second ring gear 202b are coaxially arranged in series. Further, the first ring gear 202a and the second ring gear 202b rotate relative to each other. The first planetary gears 202d mesh with the first ring gear 202 a. The second planetary gear 202e meshes with the second ring gear 202 b. Carrier 202c holds first planetary gear 202d and second planetary gear 202e rotatable and revolvable around rotation axis AL, respectively. The first planetary gear 202d and the second planetary gear 202e rotate integrally in the rotation direction. The carrier 201c of the first power planetary gear mechanism 201 and the carrier 202c of the second power planetary gear mechanism 202 are coupled to each other via a coupling shaft 203. The carrier 201c and the carrier 202c rotate integrally with the connecting shaft 203. The second power planetary gear mechanism 202 is disposed in a hollow portion of the power torque output shaft 108a and a hollow portion of the control torque output shaft 105a of the actuator 105.

The carrier 201c of the first power planetary gear mechanism 201 is coupled to the power torque output shaft 108a of the electric motor 108. The respective ring gears 201a, 201b of the first power planetary gear mechanism 201 and the

respective ring gears

202a, 202b of the second power planetary gear mechanism 202 rotate relative to the coupling shaft 203. The motive torque generated by the motive power source is transmitted to the carrier 201c via the input member 101, i.e., the motive torque output shaft 108 a. At the same time, the motive torque generated by the motive power source is transmitted to the carrier 202c via the motive torque output shaft 108a and the coupling shaft 203. Therefore, the carrier 201c and the carrier 202c become the power input element 111 of the differential mechanism 102.

The first ring gear 201a of the first power planetary gear mechanism 201 is coupled to the first drive shaft 103. A part of the power torque transmitted to the differential mechanism 102 is output from the first ring gear 201a to the first drive shaft 103. Therefore, the first ring gear 201a becomes the first power output element 112 of the differential mechanism 102.

The second ring gear 201b of the first power planetary gear mechanism 201 is coupled to the first carrier 193 of the reversing mechanism 106. A part of the control torque transmitted from the actuator 105 to the first carrier 193 of the reversing mechanism 106 acts as a reaction force against the power torque transmitted from the power input element 111 to the first power output element 112. Therefore, the second ring gear 201b serves as the first differential reaction element 113 of the differential mechanism 102.

The first ring gear 202a of the second power planetary gear mechanism 202 is coupled to the second drive shaft 104. A part of the power torque transmitted to the differential mechanism 102 is output from the first ring gear 202a to the second drive shaft 104. Therefore, the first ring gear 202a becomes the second power output element 114 of the differential mechanism 102.

The second ring gear 202b of the second power planetary gear mechanism 202 is coupled to the second carrier 194 of the reversing mechanism 106. A part of the control torque transmitted from the actuator 105 to the second carrier 194 of the reversing mechanism 106 acts as a reaction force against the power torque transmitted from the power input element 111 to the second power output element 114. Therefore, the second ring gear 202b becomes the second differential reaction element 115 of the differential mechanism 102.

The reversing mechanism 106 has the same configuration as the example shown in fig. 13. That is, the first ring gear 189 serves as the control input element 119 and the first gear 122, and the first carrier 193 serves as the first control output element 120, thereby constituting the first control planetary gear mechanism 117. The second ring gear 190 serves as the control input element 119 and the second gear 125, and the second carrier 194 serves as the second control output element 123, thereby constituting the second control planetary gear mechanism 118. The reversing mechanism 106 is disposed in a hollow portion of the power torque output shaft 108 a.

In the example shown in fig. 14, the first carrier 193 (the first control output element 120) of the reversing mechanism 106 is coupled to the second ring gear 201b (the first differential reaction element 113) of the differential mechanism 102. Further, the second carrier 194 (second control output element 123) of the reversing mechanism 106 is coupled to the second ring gear 202b (second differential reaction force element 115) of the differential mechanism 102. Therefore, in the torque vector distribution device TV shown in fig. 14, the differential mechanism 102 is configured without using a sun gear. Therefore, a space for disposing the sun gears corresponding to the

planetary gears

201d, 201e, 202d, and 202e is not required, and accordingly, the outer shape in the radial direction can be reduced.

[ fifteenth embodiment ]

In the torque vector distribution device TV shown in fig. 15, the differential mechanism 102 is constituted by a first power planetary gear mechanism 201 and a second power planetary gear mechanism 202, as in the case of the example shown in fig. 14 described above. The first power planetary gear mechanism 201 and the second power planetary gear mechanism 202 are both disposed on the same rotation axis AL as the first drive shaft 103 and the second drive shaft 104.

The reversing mechanism 106 includes: four sets of first planetary gears 211, second planetary gears 212, third planetary gears 213, and fourth planetary gears 214; four sun gears of a first sun gear 215, a second sun gear 216, a third sun gear 217, and a fourth sun gear 218; four ring gears of a first ring gear 219, a second ring gear 220, a third ring gear 221, and a fourth ring gear 222; and three

trucks

223, 224, and 225. The reversing mechanism 106 is disposed in a hollow portion of the power torque output shaft 108 a.

The first planetary gear 211, the second planetary gear 212, the third planetary gear 213, and the fourth planetary gear 214 are coaxially arranged in series. The first and second

planetary gears

211 and 212 and the third and fourth

planetary gears

213 and 214 rotate relative to each other.

The first sun gear 215, the second sun gear 216, the third sun gear 217, and the fourth sun gear 218 are coaxially arranged in series. The first and second sun gears 215 and 216 and the third and fourth sun gears 217 and 218 rotate integrally. The first sun gear 215, the second sun gear 216, the third sun gear 217, and the fourth sun gear 218 mesh with the first planetary gear 211, the second planetary gear 212, the third planetary gear 213, and the fourth planetary gear 214, respectively.

The first ring gear 219, the second ring gear 220, the third ring gear 221, and the fourth ring gear 222 are coaxially arranged in series. The first and second ring gears 219 and 220 and the third and fourth ring gears 221 and 222 rotate integrally. The first, second, third and fourth ring gears 219, 220, 221 and 222 are engaged with the first, second, third and fourth

planetary gears

211, 212, 213 and 214, respectively.

The first carrier 223, the second carrier 224, and the third carrier 225 are coaxially arranged in series. The first and second wheel frames 223, 224 and the third wheel frame 225 rotate relative to each other. The first carrier 223 holds the first planetary gear 211 to be rotatable and revolvable. The second carrier 224 holds the second planetary gears 212 to be rotatable and revolvable. The third carrier 225 holds the third planetary gears 213 and the fourth planetary gears 214 rotatably and revolvably, respectively.

The ring gears 219, 220, 221, and 222 are coupled to the control torque output shaft 105a of the actuator 105. The first carrier 223 is coupled to the second sun gear 109b, that is, the first differential reaction element 113 of the differential mechanism 102. The first sun gear 215 and the first ring gear 219 together mesh with the first planetary gears 211. The second carrier 224 is coupled to the second sun gear 110b, i.e., the second differential reaction element 115 of the differential mechanism 102. The second sun gear 216 and the second ring gear 220 together mesh with the second planet gears 212.

Therefore, the first ring gear 219 serves as the control input element 119 and the first gear 122, and the first carrier 223 serves as the first control output element 120, thereby constituting the first control planetary gear mechanism 117. The second ring gear 220 serves as the control input element 119 and the second gear 125, and the second carrier 224 serves as the second control output element 123, thereby constituting the second control planetary gear mechanism 118.

In the example shown in fig. 15, the gear ratio of the first gear train 226 including the first planetary gears 211, the first gear 122 (i.e., the first ring gear 219), and the first sun gear 215 and the gear ratio of the second gear train 227 including the second planetary gears 212, the second gear 125 (i.e., the second ring gear 220), and the second sun gear 216 are different from each other. Specifically, the gear ratios of the gear pairs of the first planetary gears 211, the first ring gear 219, and the first sun gear 215 in the first gear train 226 and the gear ratios of the gear pairs of the second planetary gears 212, the second ring gear 220, and the second sun gear 216 in the second gear train 227 are different from each other.

More specifically, the number of teeth of the first planetary gear 211 and the number of teeth of the second planetary gear 212 and the number of teeth of the third planetary gear 213 and the number of teeth of the fourth planetary gear 214 are all equal. The number of teeth of the third sun gear 217 is equal to that of the fourth sun gear 218. The number of teeth of the first sun gear 215 is smaller than those of the third sun gear 217 and the fourth sun gear 218. In addition, the number of teeth of the second sun gear 216 is greater than those of the third sun gear 217 and the fourth sun gear 218. The number of teeth of the third ring gear 221 is equal to that of the fourth ring gear 222. The number of teeth of the first ring gear 219 is larger than those of the third ring gear 221 and the fourth ring gear 222. Further, the number of teeth of the second ring gear 220 is smaller than the number of teeth of the third ring gear 221 and the fourth ring gear 222.

For example, in the example shown in fig. 15, the number of teeth of the first sun gear 215 is "29", the number of teeth of the second sun gear 216 is "31", the numbers of teeth of the third sun gear 217 and the fourth sun gear 218 are "30", the number of teeth of the first ring gear 219 is "67", the number of teeth of the second ring gear 220 is "65", and the numbers of teeth of the third ring gear 221 and the fourth ring gear 222 are "66". In this case, the reduction ratio R is "R ═ 30". A relatively large reduction ratio is obtained compared to the reduction ratio that can be achieved with a conventional general planetary gear mechanism, which is approximately 4 to 10 or so.

In the example shown in fig. 15, the first carrier 223 (the first control output element 120) of the reversing mechanism 106 is coupled to the second ring gear 201b (the first differential reaction force element 113) of the differential mechanism 102. Further, the second carrier 224 (second control output element 123) of the reversing mechanism 106 is linked to the second ring gear 202b (second differential reaction force element 115) of the differential mechanism 102. Therefore, in the torque vector distribution device TV shown in fig. 15, the differential mechanism 102 is configured without using a sun gear. Therefore, a space for disposing the sun gears corresponding to the

planetary gears

The order of arrangement of the first planetary gears 211, the second planetary gears 212, the third planetary gears 213, and the fourth planetary gears 214, the first sun gear 215, the second sun gear 216, the third sun gear 217, and the fourth sun gear 218, the first ring gear 219, the second ring gear 220, the third ring gear 221, and the fourth ring gear 222, and the first carrier 223, the second carrier 224, and the third carrier 225 is not limited to the order shown in fig. 15. For example, the first planetary gears 211, the first sun gear 215, the first ring gear 219, and the first carrier 223 may be arranged alternately with the second planetary gears 212, the second sun gear 216, the second ring gear 220, and the second carrier 224.

[ sixteenth embodiment ]

In the torque vector distribution device TV shown in fig. 16, the differential mechanism 102 is constituted by a first power planetary gear mechanism 201 and a second power planetary gear mechanism 202, as in the case of the above-described examples shown in fig. 14 and 15. The first power planetary gear mechanism 201 and the second power planetary gear mechanism 202 are both disposed on the same rotation axis AL as the first drive shaft 103 and the second drive shaft 104.

The reversing mechanism 106 includes: three sets of first, second, and third

planetary gears

231, 232, and 233; three sun gears, a first sun gear 234, a second sun gear 235, and a third sun gear 236; three ring gears of a first ring gear 237, a second ring gear 238, and a third ring gear 239; and three wheel frames, a first wheel frame 240, a second wheel frame 241, and a third wheel frame 242. The reversing mechanism 106 is disposed in a hollow portion of the power torque output shaft 108 a.

The first planetary gear 231, the second planetary gear 232, and the third planetary gear 233 are coaxially arranged in series. The first and second

planetary gears

231 and 232 and the third planetary gear 233 rotate relative to each other.

The first sun gear 234, the second sun gear 235, and the third sun gear 236 are coaxially arranged in series. The first and second sun gears 234 and 235 and the third sun gear 236 are integrally rotated. The first sun gear 234, the second sun gear 235, and the third sun gear 236 are engaged with the first planetary gears 231, the second planetary gears 232, and the third planetary gears 233, respectively.

The first ring gear 237, the second ring gear 238, and the third ring gear 239 are coaxially arranged in series. The first ring gear 237 and the second ring gear 238 and the third ring gear 239 each rotate integrally. The first, second, and third ring gears 237, 238, and 239 mesh with the first, second, and third

planetary gears

231, 232, and 233, respectively.

The first carrier 240, the second carrier 241, and the third carrier 242 are coaxially arranged in series. The first wheel frame 240, the second wheel frame 241 and the third wheel frame 242 rotate relative to each other. The first carrier 240 holds the first planetary gears 231 to be rotatable and revolvable. The second carrier 241 holds the second planetary gears 232 so as to be rotatable and revolvable. The third carrier 242 holds the third planetary gears 233 so as to be rotatable and revolvable.

The ring gears 237, 238, 239 are coupled to the control torque output shaft 105a of the actuator 105. The first carrier 240 is coupled to the second sun gear 109b, i.e., the first differential reaction element 113 of the differential mechanism 102. The first sun gear 234 and the first ring gear 237 mesh together with the first planetary gears 231. The second carrier 241 is coupled to the second sun gear 110b, that is, the second differential reaction element 115 of the differential mechanism 102. The second sun gear 235 and the second ring gear 238 together mesh with the second planetary gears 232.

Therefore, the first ring gear 237 serves as the control input element 119 and the first gear 122, and the first carrier 240 serves as the first control output element 120, thereby constituting the first control planetary gear mechanism 117. The second ring gear 238 serves as the control input element 119 and the second gear 125, and the second carrier 241 serves as the second control output element 123, thereby constituting the second control planetary gear mechanism 118.

In the example shown in fig. 16, the gear ratio of the first gear train 243 including the first planetary gears 231, the first gear 122 (i.e., the first ring gear 237) and the first sun gear 234 and the gear ratio of the second gear train 244 including the second planetary gears 232, the second gear 125 (i.e., the second ring gear 238) and the second sun gear 235 are different from each other. Specifically, the gear ratios of the gear pairs of the first planetary gears 231, the first ring gear 237, and the first sun gear 234 in the first gear train 243 and the gear ratios of the gear pairs of the second planetary gears 232, the second ring gear 238, and the second sun gear 235 in the second gear train 244 are different from each other.

More specifically, the number of teeth of the first planetary gear 231, the number of teeth of the second planetary gear 232, and the number of teeth of the third planetary gear 233 are all equal. The number of teeth of the first sun gear 234 is smaller than that of the third sun gear 236. In addition, the number of teeth of the second sun gear 235 is greater than that of the third sun gear 236. The number of teeth of the first ring gear 237 is larger than that of the third ring gear 239. Further, the number of teeth of the second ring gear 238 is smaller than that of the third ring gear 239.

For example, in the example shown in fig. 16, the number of teeth of the first sun gear 234 is "29", the number of teeth of the second sun gear 235 is "31", the number of teeth of the third sun gear 236 is "30", the number of teeth of the first ring gear 237 is "67", the number of teeth of the second ring gear 238 is "65", and the number of teeth of the third ring gear 239 is "66". In this case, the reduction ratio R is "R ═ 30". A relatively large reduction ratio is obtained compared to the reduction ratio that can be achieved with a conventional general planetary gear mechanism, which is approximately 4 to 10 or so.

In the example shown in fig. 16, the first carrier 240 (the first control output element 120) of the reversing mechanism 106 is coupled to the second ring gear 201b (the first differential reaction force element 113) of the differential mechanism 102. Further, the second carrier 241 (second control output element 123) of the reversing mechanism 106 is coupled to the second ring gear 202b (second differential reaction force element 115) of the differential mechanism 102. Therefore, in the torque vector distribution device TV shown in fig. 16, the differential mechanism 102 is configured without using a sun gear. Therefore, a space for disposing the sun gears corresponding to the

planetary gears

The order of arrangement of the first, second, and third

planetary gears

231, 232, and 233, the first, second, and third sun gears 234, 235, and 236, the first, second, and third ring gears 237, 238, and 239, the first, second, and third carriers 240, 241, and 242 is not limited to the order shown in fig. 16. For example, the first planetary gear 231, the first sun gear 234, the first ring gear 237, and the first carrier 240 may be arranged alternately with the second planetary gear 232, the second sun gear 235, the second ring gear 238, and the second carrier 241.

[ seventeenth embodiment ]

In the torque vector distribution device TV shown in fig. 17, the differential mechanism 102 is constituted by the first power planetary gear mechanism 141 and the second power planetary gear mechanism 142, as in the case of the example shown in fig. 11 described above. The first power planetary gear mechanism 141 and the second power planetary gear mechanism 142 are both disposed on the same rotation axis AL as the first drive shaft 103 and the second drive shaft 104. Further, as in the example shown in fig. 11, the first output torque reduction mechanism 143, the second output torque reduction mechanism 145, and the coupling mechanism 144 are provided.

The reversing mechanism 106 includes: three sets of planet gears, a first planet gear 251, a second planet gear 252, and a third planet gear 253; three sun gears, a first sun gear 254, a second sun gear 255, and a third sun gear 256; three ring gears of a first ring gear 257, a second ring gear 258, and a third ring gear 259; and three wheel frames, a first wheel frame 260, a second wheel frame 261, and a third wheel frame 262. The reversing mechanism 106 is disposed in a hollow portion of the power torque output shaft 108 a.

The first planetary gear 251, the second planetary gear 252, and the third planetary gear 253 are coaxially arranged in series. The first planetary gears 251 and the second and third

planetary gears

252 and 253 rotate relative to each other.

The first sun gear 254, the second sun gear 255, and the third sun gear 256 are coaxially arranged in series. The first sun gear 254 and the second sun gear 255 and the third sun gear 256 rotate integrally. The first sun gear 254, the second sun gear 255, and the third sun gear 256 are engaged with the first planetary gears 251, the second planetary gears 252, and the third planetary gears 253, respectively.

The first ring gear 257, the second ring gear 258, and the third ring gear 259 are coaxially arranged in series. The first ring gear 257 and the second and third ring gears 258 and 259 each rotate integrally. The first, second, and third ring gears 257, 258, and 259 mesh with the first, second, and third

planetary gears

251, 252, and 253, respectively.

The first carrier 260, the second carrier 261, and the third carrier 262 are coaxially arranged in series. The first and second wheel frames 260, 261 and the third wheel frame 262 rotate relative to each other. The first carrier 260 holds the first planetary gear 251 to be rotatable and revolvable. The second carrier 261 holds the second planetary gear 252 so as to be rotatable and revolvable. The third carrier 262 keeps the third planetary gears 253 rotatable and revolvable.

Each of the ring gears 257, 258, 259 is coupled to the control torque output shaft 105a of the actuator 105. The first carrier 260 is coupled to the second sun gear 109b, i.e., the first differential reaction element 113 of the differential mechanism 102. The first sun gear 254 and the first ring gear 257 together mesh with the first planetary gears 251. The second carrier 261 is coupled to the second sun gear 110b, that is, the second differential reaction element 115 of the differential mechanism 102. The second sun gear 255 and the second ring gear 258 together mesh with the second planetary gears 252.

Therefore, the first ring gear 257 serves as the control input element 119 and the first gear 122, and the first carrier 260 serves as the first control output element 120, thereby constituting the first control planetary gear mechanism 117. The second ring gear 258 serves as the control input element 119 and the second gear 125, and the second carrier 261 serves as the second control output element 123, thereby constituting the second control planetary gear mechanism 118.

In the example shown in fig. 17, the gear ratio of the first gear train 263 including the first planetary gears 251 and the first gear 122 (i.e., the first ring gear 257) and the gear ratio of the second gear train 264 including the second planetary gears 252 and the second gear 125 (i.e., the second ring gear 258) are different from each other. Specifically, the gear ratios of the gear pairs of the first ring gear 257, the first planetary gears 251, and the first sun gear 254 in the first gear train 263 and the gear ratios of the gear pairs of the second ring gear 258, the second planetary gears 252, and the second sun gear 255 in the second gear train 264 are different from each other.

More specifically, the number of teeth of the first ring gear 257, the number of teeth of the second ring gear 258, and the number of teeth of the third ring gear 259 are all equal. The number of teeth of the first planetary gear 251 is less than that of the third planetary gear 253, and the number of teeth of the second planetary gear 252 is greater than that of the third planetary gear 253. The number of teeth of the first sun gear 254 is greater than that of the third sun gear 256, and the number of teeth of the second sun gear 255 is less than that of the third sun gear 256.

For example, in the example shown in fig. 17, the number of teeth of each of the ring gears 257, 258, 259 is "90", the number of teeth of the first sun gear 254 is "45", the number of teeth of the second sun gear 255 is "18", and the number of teeth of the third sun gear 256 is "30". In this case, the reduction ratio R becomes "R ═ 3". In the torque vector distribution device TV shown in fig. 17, for example, the obtained reduction ratio is relatively small as compared with the example shown in fig. 10. However, in the example shown in fig. 17, the load applied to the reversing mechanism 106 is reduced, and therefore the reversing mechanism 106 can be made smaller. Therefore, the torque vector distribution device TV can be downsized.

Note that the order of arrangement of the first planetary gears 251, the second planetary gears 252, and the third planetary gears 253, the first sun gear 254, the second sun gear 255, and the third sun gear 256, the first ring gear 257, the second ring gear 258, and the third ring gear 259, and the first carrier 260, the second carrier 261, and the third carrier 262 is not limited to the order shown in fig. 17. For example, the first planetary gear 251, the first sun gear 254, the first ring gear 257, and the first carrier 260 may be arranged alternately with the second planetary gear 252, the second sun gear 255, the second ring gear 258, and the second carrier 261.

[ eighteenth embodiment ]

In the torque vector distribution device TV shown in fig. 18, the differential mechanism 102 is constituted by the first power planetary gear mechanism 141 and the second power planetary gear mechanism 142, as in the case of the example shown in fig. 11 described above. The first power planetary gear mechanism 141 and the second power planetary gear mechanism 142 are both disposed on the same rotation axis AL as the first drive shaft 103 and the second drive shaft 104. Further, as in the example shown in fig. 11, the first output torque reduction mechanism 143, the second output torque reduction mechanism 145, and the coupling mechanism 144 are provided.

The reversing mechanism 106 includes: three sets of planet gears of a first planet gear 271, a second planet gear 272, and a third planet gear 273; three sun gears, a first sun gear 274, a second sun gear 275, and a third sun gear 276; a ring gear 277; and two wheel frames, a first wheel frame 278 and a second wheel frame 279. The reversing mechanism 106 is disposed in a hollow portion of the power torque output shaft 108 a.

The first planetary gear 271, the second planetary gear 272, and the third planetary gear 273 are coaxially arranged in series. The first planetary gears 271 and the third planetary gears 273 rotate integrally in the rotation direction. The first and third

planetary gears

271, 273 and the second planetary gears 272 rotate relative to each other.

The first sun gear 274, the second sun gear 275, and the third sun gear 276 are coaxially arranged in series. The first sun gear 274 and the third sun gear 276 rotate relative to each other. In addition, the second sun gear 275 and the third sun gear 276 rotate relatively. The first sun gear 274, the second sun gear 275, and the third sun gear 276 are meshed with the first planetary gear 271, the second planetary gear 272, and the third planetary gear 273, respectively. The third sun gear 276 is fixed against rotation. In the example shown in fig. 18, the third sun gear 276 is fixed to the housing 107.

The ring gear 277 meshes with the second planetary gears 272. The ring gear 277 is fixed against rotation. In the example shown in fig. 18, the ring gear 277 is fixed to the housing 107.

The first wheel frame 278 and the second wheel frame 279 are coaxially arranged in series. The first wheel frame 278 and the second wheel frame 279 rotate relative to each other. The first carrier 278 holds the first planetary gears 271 and the third planetary gears 273 to be rotatable and revolvable, respectively. The second carrier 279 retains the second planetary gears 272 rotatably and revolvably. The first carrier 278 is coupled to the second sun gear 275.

The first carrier 278 is coupled to a control torque output shaft 105a of the actuator 105. The first sun gear 274 is coupled to the second sun gear 109b, that is, the first differential reaction element 113 of the differential mechanism 102. The first sun gear 274 and the first planetary gears 271 mesh with each other. The second wheel frame 279 is coupled to the second sun gear 110b, that is, the second differential reaction element 115 of the differential mechanism 102. The second sun gear 275 and the ring gear 277 mesh together with the second planetary gears 272.

Therefore, the first carrier 278 serves as the control input element 119, the first sun gear 274 serves as the first control output element 120 and the first gear 122, and the first control planetary gear mechanism 117 is configured. The second sun gear 275 serves as the control input element 119 and the second gear 125, and the second carrier 279 serves as the second control output element 123, thereby constituting the second control planetary gear mechanism 118.

In the example shown in fig. 18, the gear ratio of the first gear train 280 including the first planetary gears 271 and the first gear 122 (i.e., the first sun gear 274) and the gear ratio of the second gear train 281 including the second planetary gears 272 and the second gear 125 (i.e., the second sun gear 275) are different from each other. Specifically, the gear ratios of the gear pairs of the first planetary gears 271 and the first sun gear 274 in the first gear train 280 and the gear ratios of the gear trains of the ring gear 277, the second planetary gears 272, and the second sun gear 275 in the second gear train 281 are different from each other. In other words, the gear ratio of the gear transmission path 282, in which the control torque of the actuator 105 is transmitted to the first differential reaction element 113 of the differential mechanism 102 via the first carrier 278, the first planetary gears 271, and the first sun gear 274, and the gear ratio of the gear transmission path 283, in which the control torque of the actuator 105 is transmitted to the second differential reaction element 115 of the differential mechanism 102 via the first carrier 278, the second sun gear 275, the second planetary gears 272, and the second carrier 279, are different from each other.

For example, in the example shown in fig. 18, the number of teeth of the first sun gear 274 is "20", the number of teeth of the first planetary gear 271 is "25", the number of teeth of the second sun gear 275 is "30", the number of teeth of the second planetary gear 272 is "30", and the number of teeth of the ring gear 277 is "90". The number of teeth of the third sun gear 276 is "20", and the number of teeth of the third planetary gears 273 is "20". As a result, the gear ratio of the gear pair of the first sun gear 274 and the first planetary gears 271, that is, the gear ratio of the gear transmission path 282, and the gear ratio of the gear train (planetary gear mechanism) of the second sun gear 275, the second planetary gears 272, and the ring gear 277, that is, the gear ratio of the gear transmission path 283, are different from each other. In this case, the reduction ratio R is "R ═ 4". In the torque vector distribution device TV shown in fig. 18, the obtained reduction ratio is relatively small as compared with the example shown in fig. 10, for example. However, in the example shown in fig. 18, the load applied to the reversing mechanism 106 is reduced as in the example shown in fig. 17 described above, and therefore, the reversing mechanism 106 can be made smaller. Therefore, the torque vector distribution device TV can be downsized.

The order of arrangement of the first planetary gears 271, the second planetary gears 272, and the third planetary gears 273, the first sun gear 274, the second sun gear 275, and the third sun gear 276, the ring gear 277, and the first carrier 278 and the second carrier 279 described above is not limited to the order shown in fig. 18. For example, the first planetary gears 271 and the third planetary gears 273, the first sun gear 274 and the third sun gear 276, and the first carrier 278 may be arranged alternately with the second planetary gears 272, the second sun gear 275, the ring gear 277, and the second carrier 279.

[ nineteenth embodiment ]

In the torque vector distribution device TV shown in fig. 19, the differential mechanism 102 is constituted by the first power planetary gear mechanism 161 and the second power planetary gear mechanism 162, as in the case of the example shown in fig. 12 described above. The first power planetary gear mechanism 161 and the second power planetary gear mechanism 162 are both disposed on the same rotation axis AL as the first drive shaft 103 and the second drive shaft 104. Further, as in the example shown in fig. 12, a gear train 165 and a gear train 168 are provided. Further, as in the example shown in fig. 12 described above, the electric motors 108 as the power sources have the first power torque output shaft 108b and the second power torque output shaft 108c, which are coaxially spaced apart and protrude in the left-right direction.

In the example shown in fig. 19, the actuator 105 has a first rotation shaft 105b and a second rotation shaft 105c as the control torque output shaft 105 a. The first rotation shaft 105b and the second rotation shaft 105c are arranged coaxially and in a left-right opposed manner. The first rotation shaft 105b protrudes toward the first drive shaft 103 (left side in fig. 19). A first sun gear 293 of an inversion mechanism 106 described later is attached to a protruding portion of the first rotation shaft 105 b. The second rotation shaft 105c protrudes toward the second drive shaft 104 (right side in fig. 19). A second sun gear 294 of the reversing mechanism 106, which will be described later, is fitted to a protruding portion of the second rotation shaft 105 c.

The reversing mechanism 106 includes: two sets of planet gears, a first planet gear 291 and a second planet gear 292; two sun gears, a first sun gear 293 and a second sun gear 294; two ring gears of a first ring gear 295 and a second ring gear 296; and two wheel frames, a first wheel frame 297 and a second wheel frame 298.

The first planetary gear 291 and the second planetary gear 292 are coaxially arranged in series. The first planetary gear 291 and the second planetary gear 292 rotate relative to each other.

The first sun gear 293 and the second sun gear 294 are coaxially arranged in series. The first sun gear 293 and the second sun gear 294 rotate relative to each other. The first sun gear 293 and the second sun gear 294 are engaged with the first planetary gear 291 and the second planetary gear 292, respectively.

The first ring gear 295 and the second ring gear 296 are coaxially arranged in series. The second ring gear 296 rotates relative to the first ring gear 295. The first ring gear 295 and the second ring gear 296 are meshed with the first planetary gear 291 and the second planetary gear 292, respectively. The first ring gear 295 is fixed against rotation. In the example shown in fig. 19, the first ring gear 295 is fixed to the housing 107.

The first wheel carriage 297 and the second wheel carriage 298 are coaxially arranged in series. The first wheel carriage 297 and the second wheel carriage 298 rotate relative to each other. The first carrier 297 holds the first planetary gears 291 rotatably and revolvably. The second carrier 298 holds the second planetary gears 292 to be rotatable. The second wheel carriage 298 is fixed against rotation. In the example shown in fig. 19, the second carrier 298 is fixed to the housing 107.

The first sun gear 293 is coupled to the first rotating shaft 105b (control torque output shaft 105a) of the actuator 105. The first carrier 297 is coupled to the sun gear 161a of the first power planetary gear mechanism 161, that is, the first differential reaction element 113 of the differential mechanism 102. The first sun gear 293 and the first ring gear 295 mesh together with the first planetary gears 291. The second sun gear 294 is coupled to the second rotary shaft 105c (control torque output shaft 105a) of the actuator 105. The second ring gear 296 is coupled to the sun gear 162a of the second power planetary gear mechanism 162, that is, the second differential reaction element 115 of the differential mechanism 102. The second sun gear 294 and the second ring gear 296 together mesh with the second planet gears 292.

Therefore, the first sun gear 293 serves as the control input element 119 and the first gear 122, and the first carrier 297 serves as the first control output element 120, thereby constituting the first control planetary gear mechanism 117. The second sun gear 294 serves as the control input element 119, and the second ring gear 296 serves as the second control output element 123 and the second gear 125, thereby constituting the second control planetary gear mechanism 118.

In the example shown in fig. 19, the gear ratio of the first gear train 299 including the first planetary gear 291 and the first gear 122 (i.e., the first sun gear 293) and the gear ratio of the second gear train 300 including the second planetary gear 292 and the second gear 125 (i.e., the second ring gear 296) are different from each other. Specifically, the gear ratio of the first gear train 299 including the first sun gear 293, the first planetary gears 291, and the first ring gear 295 and the gear ratio of the second gear train 300 including the second sun gear 294, the second planetary gears 292, and the second ring gear 296 are different from each other. In other words, the gear ratio of the gear transmission path 301 in which the control torque of the actuator 105 is transmitted to the first differential reaction element 113 of the differential mechanism 102 via the first sun gear 293, the first planetary gear 291, and the first carrier 297, and the gear ratio of the gear transmission path 302 in which the control torque of the actuator 105 is transmitted to the second differential reaction element 115 of the differential mechanism 102 via the second sun gear 294, the second planetary gear 292, and the second ring gear 296, are different from each other.

For example, in the example shown in fig. 19, the number of teeth of the first sun gear 293 is "30", the number of teeth of the first ring gear 295 is "90", the number of teeth of the second sun gear 294 is "24", and the number of teeth of the second ring gear 296 is "96". As a result, the gear ratio of the gear transmission path 301 and the gear ratio of the gear transmission path 302 are different from each other. In this case, the reduction ratio R is "R ═ 4". In the torque vector distribution device TV shown in fig. 19, the obtained reduction ratio is relatively small as compared with the example shown in fig. 10, for example. However, in the example shown in fig. 19, the load applied to the reversing mechanism 106 is reduced as in the examples shown in fig. 17 and 18 described above, and therefore the reversing mechanism 106 can be made smaller. Therefore, the torque vector distribution device TV can be downsized.

The order of arrangement of the first and second

planetary gears

291 and 292, the first and second sun gears 293 and 294, the first and second ring gears 295 and 296, and the first and second carriers 297 and 298 is not limited to the order shown in fig. 19. For example, the first planetary gear 291, the first sun gear 293, the first ring gear 295, and the first carrier 297 may be arranged alternately with the second planetary gear 292, the second sun gear 294, the second ring gear 296, and the second carrier 298.

[ twentieth embodiment, twenty-first embodiment, twenty-second embodiment ]

The reversing mechanisms 106 in the torque vector distribution devices TV shown in fig. 20, 21, and 22 are each constituted by a compound planetary gear mechanism disposed so as to be separated from each other in the right-left direction.

In the example shown in fig. 20, the reversing mechanism 106 is constituted by a first control planetary gear mechanism 311 and a second control planetary gear mechanism 312. The first control planetary gear mechanism 311 and the second control planetary gear mechanism 312 are both disposed on the same rotation axis AL as the first drive shaft 103 and the second drive shaft 104.

The first control planetary gear mechanism 311 and the second control planetary gear mechanism 312 are each constituted by a compound planetary gear mechanism in which two planetary gear mechanisms are combined.

The first control planetary gear mechanism 311 has a first sun gear 311a, a second sun gear 311b, a first ring gear 311c, a second ring gear 311d, a first carrier 311e, and a second carrier 311 f. The first sun gear 311a and the second sun gear 311b are coaxially arranged in series. The first sun gear 311a rotates integrally with the second sun gear 311 b. The first ring gear 311c and the second ring gear 311d are coaxially arranged in series. The first ring gear 311c rotates integrally with the second ring gear 311 d. The first carrier 311e and the second carrier 311f are coaxially arranged in series. The first carrier 311e is fixed so as not to rotate. The second carrier 311f rotates relative to the first carrier 311 e.

The first sun gear 311a and the second sun gear 311b are coupled to the first rotating shaft 105b (control torque output shaft 105a) of the actuator 105. The second carrier 311f is coupled to the sun gear 161a of the first power planetary gear mechanism 161, that is, the first differential reaction element 113 of the differential mechanism 102.

The second control planetary gear mechanism 312 has a first sun gear 312a, a second sun gear 312b, a first ring gear 312c, a second ring gear 312d, a first carrier 312e, and a second carrier 312 f. The first sun gear 312a and the second sun gear 312b are coaxially arranged in series. The first sun gear 312a rotates integrally with the second sun gear 312 b. The first ring gear 312c and the second ring gear 312d are coaxially arranged in series. The first ring gear 312c rotates integrally with the second ring gear 312 d. The first carrier 312e and the second carrier 312f are coaxially arranged in series. The first carrier 312e is fixed so as not to rotate. The second carrier 312f rotates relative to the first carrier 312 e.

The first sun gear 312a and the second sun gear 312b are coupled to the second rotation shaft 105c (control torque output shaft 105a) of the actuator 105. The second carrier 312f is coupled to the sun gear 162a of the second power planetary gear mechanism 162, that is, the second differential reaction element 115 of the differential mechanism 102.

In the example shown in fig. 21, the reversing mechanism 106 is constituted by a first control planetary gear mechanism 321 and a second control planetary gear mechanism 322. The first control planetary gear mechanism 321 and the second control planetary gear mechanism 322 are both disposed on the same rotation axis AL as the first drive shaft 103 and the second drive shaft 104.

The first control planetary gear mechanism 321 and the second control planetary gear mechanism 322 are each constituted by a compound planetary gear mechanism in which two planetary gear mechanisms are combined.

The first control planetary gear mechanism 321 has a sun gear 321a, a first ring gear 321b, a second ring gear 321c, a first carrier 321d, and a second carrier 321 e. The first ring gear 321b and the second ring gear 321c are coaxially arranged in series. The first ring gear 321b is fixed so as not to be rotatable. The second ring gear 321c rotates relative to the first ring gear 321 b. The first carrier 321d and the second carrier 321e are coaxially arranged in series. The first carrier 321d and the second carrier 321e rotate relative to each other.

The sun gear 321a is coupled to the first rotating shaft 105b (control torque output shaft 105a) of the actuator 105. The second ring gear 321c is coupled to the sun gear 161a of the first power planetary gear mechanism 161, that is, the first differential reaction element 113 of the differential mechanism 102.

The second control planetary gear mechanism 322 has a sun gear 322a, a first ring gear 322b, a second ring gear 322c, a first carrier 322d, and a second carrier 322 e. The first ring gear 322b and the second ring gear 322c are coaxially arranged in series. The first ring gear 322b is fixed so as not to be rotatable. The second ring gear 322c rotates relative to the first ring gear 322 b. The first carrier 322d and the second carrier 322e are coaxially arranged in series. The first and second wheel frames 322d and 322e rotate relative to each other.

The sun gear 322a is coupled to the second rotation shaft 105c (control torque output shaft 105a) of the actuator 105. The second ring gear 322c is coupled to the sun gear 162a of the second power planetary gear mechanism 162, that is, the second differential reaction element 115 of the differential mechanism 102.

In the example shown in fig. 22, the reversing mechanism 106 is constituted by a first control planetary gear mechanism 331 and a second control planetary gear mechanism 332. The first control planetary gear mechanism 331 and the second control planetary gear mechanism 332 are both disposed on the same rotation axis AL as the first drive shaft 103 and the second drive shaft 104.

The first control planetary gear mechanism 331 and the second control planetary gear mechanism 332 are each constituted by a compound planetary gear mechanism in which two planetary gear mechanisms are combined.

The first control planetary gear mechanism 331 has a first sun gear 331a, a second sun gear 331b, a ring gear 331c, a first carrier 331d, and a second carrier 331 e. The first sun gear 331a and the second sun gear 331b are coaxially arranged in series. The first and second sun gears 331a and 331b rotate relative to each other. The first wheel frame 331d and the second wheel frame 331e are coaxially arranged in series. The first wheel frame 331d and the second wheel frame 331e rotate relative to each other.

The ring gear 331c is coupled to the first rotation shaft 105b (control torque output shaft 105a) of the actuator 105. The second sun gear 331b is coupled to the sun gear 161a of the first power planetary gear mechanism 161, that is, the first differential reaction element 113 of the differential mechanism 102. The first sun gear 331a is coupled to the first sun gear 332a of the second control planetary gear mechanism 332. The first sun gear 331a rotates integrally with the first sun gear 332 a.

The second control planetary gear mechanism 332 has a first sun gear 332a, a second sun gear 332b, a ring gear 332c, a first carrier 332d, and a second carrier 332 e. The first sun gear 332a and the second sun gear 332b are coaxially arranged in series. The first sun gear 332a and the second sun gear 332b rotate relative to each other. The first carrier 332d and the second carrier 332e are coaxially arranged in series. The first and

second carriers

332d and 332e rotate relative to each other.

The ring gear 332c is coupled to the second rotating shaft 105c (control torque output shaft 105a) of the actuator 105. The second sun gear 332b is coupled to the sun gear 162a of the second power planetary gear mechanism 162, that is, the second differential reaction element 115 of the differential mechanism 102.

The differential mechanism 102 in each of the torque vector distribution devices TV of the tenth embodiment (fig. 10), the eleventh embodiment (fig. 11), the twelfth embodiment (fig. 12), the thirteenth embodiment (fig. 13), the fourteenth embodiment (fig. 14), the fifteenth embodiment (fig. 15), the sixteenth embodiment (fig. 16), the seventeenth embodiment (fig. 17), the eighteenth embodiment (fig. 18), the nineteenth embodiment (fig. 19), the twentieth embodiment (fig. 20), the twenty-first embodiment (fig. 21), and the twenty-second embodiment (fig. 22) described above is connected to the input member 101 and the power input element 111. The first power output element 112 is coupled to the first drive shaft 103. The second power output member 114 is coupled to the second drive shaft 104. Further, the first differential reaction force element 113 and the second differential reaction force element 115 are coupled to the actuator 105 via the reversing mechanism 106. The reversing mechanism 106 in each of the torque vector distribution devices TV of the tenth embodiment to the twenty-second embodiment described above is coupled to the control input element 119 through the actuator 105. The first gear 122 forms the control input member 119 or the first control output member 120. The second gear 125 forms the control input element 119 or the second control output element 123. Also, the reversing mechanisms 106 are each configured to amplify and transmit the control torque input to the control input element 119 to the first differential reaction element 113 and the second differential reaction element 115.

Therefore, according to the torque vector distribution devices TV of the tenth to twenty-second embodiments described above, the control torque of the actuator 105 can be amplified by the reaction mechanism 6 and transmitted to the first differential reaction element 113 and the second differential reaction element 115 of the differential mechanism 102. Therefore, the actuator 5 can be downsized in accordance with the amplification of the control torque by the deceleration function of the reversing mechanism 6. Further, the torque vector distribution device TV can be downsized in its outer shape. As a result, the downsized torque vector distribution device TV can be easily mounted on the vehicle.

In each of the torque vector distribution devices TV of the tenth embodiment (fig. 10), the twelfth embodiment (fig. 12), the thirteenth embodiment (fig. 13), the fourteenth embodiment (fig. 14), the fifteenth embodiment (fig. 15), the sixteenth embodiment (fig. 16), the nineteenth embodiment (fig. 19), the twentieth embodiment (fig. 20), the twenty-first embodiment (fig. 21), and the twenty-second embodiment (fig. 22) described above, the differential mechanism 102 forms a reduction gear mechanism in which the first control planetary gear mechanism 117 (or 311, 321, 331) and the second control planetary gear mechanism 118 (or 312, 322, 332) amplify the control torque. In the inverting mechanism 106 of each of the torque vector distribution devices TV described above, the control torque amplified by the first control planetary gear mechanism 117 (or 311, 321, 331) is transmitted to the first differential reaction element 113, and the control torque amplified by the second control planetary gear mechanism 118 (or 312, 322, 332) is transmitted to the second differential reaction element 115. Therefore, a relatively large reduction ratio is obtained in the reversing mechanism 106. Therefore, in each of the torque vector distribution devices TV described above, the actuator 5 can be downsized by the deceleration function (torque amplification action) of the reversing mechanism 106, and the outer shape of the torque vector distribution device TV can be downsized.

Each of the torque vector distribution devices TV of the eleventh embodiment (fig. 11), the seventeenth embodiment (fig. 17), and the eighteenth embodiment (fig. 18) described above includes a first output torque reduction mechanism 143 and a second output torque reduction mechanism 145 which are coaxially disposed so as to face left and right, the first output torque reduction mechanism 143 amplifying the torque transmitted to the first drive shaft 103, and the second output torque reduction mechanism 145 amplifying the torque transmitted to the second drive shaft 104. In the differential mechanism 102 in each torque vector distribution device TV described above, the first power output element 112 and the first drive shaft 103 are coupled via the first output torque reduction mechanism 143. The second power output element 114 and the second drive shaft 104 are coupled via a second output torque reduction mechanism 145. Further, the reversing mechanism 106 in each of the torque-vector distribution devices TV described above is disposed between the first output-torque speed reduction mechanism 143 and the second output-torque speed reduction mechanism 145 in the direction of the rotation axis AL. Therefore, in the reversing mechanism 106, although the obtained reduction ratio is relatively small, the load applied to the reversing mechanism 106 is low. Therefore, in each of the torque vector distribution devices TV described above, the actuator 5 can be downsized in accordance with the reduction in the load of the reversing mechanism 106, and the outer shape of the torque vector distribution device TV can be downsized.

Claims

1. A torque vector distribution device is provided with: an input member to which power torque is input from a power source; a first drive shaft and a second drive shaft which are coaxially arranged to face each other in the left-right direction and are rotatable relative to each other; a differential mechanism that, between the input member and the first and second drive shafts, distributes and transmits the motive torque input to the input member to the first and second drive shafts, and enables differential rotation of the first and second drive shafts; an actuator that imparts a control torque to the differential mechanism to differentially rotate the first drive shaft and the second drive shaft; and a reverse rotation mechanism that rotates the first drive shaft and the second drive shaft in directions opposite to each other when the first drive shaft and the second drive shaft are differentially rotated,

the torque vector distribution device is characterized in that,

the differential mechanism is composed of a first power planetary gear mechanism and a second power planetary gear mechanism which are coaxially arranged in a left-right opposite manner,

the first power planetary gear mechanism has: a power input element to which the power torque is transmitted from the input member; a first power output element that outputs the power torque to the first drive shaft; and a first differential reaction force element to which the control torque is transmitted as a reaction force to the motive torque transmitted from the motive power input element to the first motive power output element,

The second power planetary gear mechanism includes: the power input element; a second power output element that outputs the motive torque to the second drive shaft; and a second differential reaction force element to which the control torque is transmitted as a reaction force to the motive torque transmitted from the motive power input element to the second motive power output element,

the reverse mechanism is constituted by a first control planetary gear mechanism and a second control planetary gear mechanism that are arranged coaxially with the first drive shaft and the second drive shaft, respectively, the first control planetary gear mechanism transmitting the control torque to the first drive shaft via the first differential reaction element, the second control planetary gear mechanism transmitting the control torque to the second drive shaft via the second differential reaction element,

the first control planetary gear mechanism has: a control input element to which the control torque is input from the actuator; a first control output element that outputs the control torque to the first drive shaft; a first planetary gear to which the control torque is transmitted from the control input element; and a first gear meshed with the first planetary gear to form the control input element or the first control output element,

The second control planetary gear mechanism has: the control input element; a second control output element that outputs the control torque to the second drive shaft; a second planetary gear arranged coaxially with the first planetary gear, the control torque being transmitted from the control input element; and a second gear meshed with the second planetary gear to form the control input element or the second control output element,

the gear ratio of a first gear train including the first planetary gear and the first gear and the gear ratio of a second gear train including the second planetary gear and the second gear are different from each other.

2. The torque vector distribution device of claim 1,

with the reversing mechanism, both a first reduction gear ratio that represents a proportion of the rotational speed of the first control output element relative to the rotational speed of the control input element and a second reduction gear ratio that represents a proportion of the rotational speed of the second control output element relative to the rotational speed of the control input element are greater than "1",

the reverse mechanism forms a reduction gear mechanism that amplifies and transmits the control torque to the first control output element and the second control output element.

3. The torque vector distribution device according to claim 1 or 2,

with regard to the differential mechanism, it is preferable that,

the input member is coupled to the power input element,

the first power output element is coupled to the first drive shaft,

the second power output element is coupled to the second drive shaft,

with regard to the reverse-rotation mechanism, it is preferable that,

the actuator is coupled to the control input element,

the first gear forms the first control output element,

the second gear forms the second control output element,

the reverse mechanism amplifies and transmits the control torque input to the control input element to the first drive shaft and the second drive shaft.

4. The torque vector distribution device of claim 3,

the reverse rotation mechanism is rotationally linked together with the power input element and the first and second power output elements when the first drive shaft and the second drive shaft rotate in the same direction at the same speed.

5. The torque vector distribution device according to claim 3 or 4,

Comprising: a third planetary gear disposed coaxially with the first planetary gear and the second planetary gear; and

a wheel carrier for holding each of the planetary gears so as to be rotatable and revolvable,

the first planetary gear and the second planetary gear and the third planetary gear rotate integrally in a rotation direction,

the third planetary gear is transmitted the power torque from the power input element.

6. The torque vector distribution device according to claim 3 or 4,

comprising: third and fourth planet gears arranged coaxially with the first and second planet gears, respectively; and

the first planetary gear and the third planetary gear rotate integrally in a rotation direction,

the second planetary gear and the fourth planetary gear rotate integrally in a rotation direction,

the first and third planet gears and the second and fourth planet gears are rotatable relative to each other,

the third planetary gear and the fourth planetary gear are each transmitted the power torque from the power input element.

7. The torque vector distribution device of claim 5,

the differential mechanism includes:

the first, second, and third planet gears;

a first sun gear, a second sun gear, and a third sun gear arranged on a same axis, the first sun gear being in mesh with the first planetary gear, the second sun gear being in mesh with the second planetary gear, the third sun gear being in mesh with the third planetary gear; and

the wheel frame is arranged on the upper portion of the frame,

the first and second sun gears are rotatable relative to each other,

the third sun gear serves as the power input element, the first sun gear serves as the first power output element, and the carrier serves as the first differential reaction force element, thereby constituting the first power planetary gear mechanism,

the third sun gear serves as the power input element, the second sun gear serves as the second power output element, and the carrier serves as the second differential reaction force element, thereby constituting the second power planetary gear mechanism,

the reversing mechanism includes:

The first, second, and third planet gears;

the first sun gear, the second sun gear, and the third sun gear; and

the wheel frame is arranged on the upper portion of the frame,

the carrier serves as the control input element, the first sun gear serves as the first gear and serves as the first control output element, and the first control planetary gear mechanism is constituted,

the carrier serves as the control input element, and the second sun gear serves as the second gear and serves as the second control output element, thereby constituting the second control planetary gear mechanism,

the number of teeth of the first sun gear is equal to that of the second sun gear and that of the third sun gear,

the number of teeth of the first planetary gear is greater than that of the third planetary gear, and the number of teeth of the second planetary gear is less than that of the third planetary gear.

8. The torque vector distribution device of claim 5,

the differential mechanism includes:

the first, second, and third planet gears;

a first sun gear, a second sun gear, and a third sun gear arranged on a same axis, the first sun gear being in mesh with the first planetary gear, the second sun gear being in mesh with the second planetary gear, the third sun gear being in mesh with the third planetary gear;

The wheel carrier; and

an inner gear ring meshing with the third planetary gear,

the first and second sun gears are rotatable relative to each other,

the third sun gear becomes the power input element, the first sun gear becomes the first power output element, and the ring gear becomes the first differential reaction force element, thereby constituting the first power planetary gear mechanism,

the third sun gear becomes the power input element, the second sun gear becomes the second power output element, and the ring gear becomes the second differential reaction force element, thereby constituting the second power planetary gear mechanism,

the reversing mechanism includes:

the first, second, and third planet gears;

the first sun gear, the second sun gear, and the third sun gear;

the wheel carrier; and

the gear ring is provided with a gear ring which is provided with a gear ring,

the ring gear becomes the control input element, the first sun gear becomes the first gear and becomes the first control output element, and the first control planetary gear mechanism is constituted,

The ring gear becomes the control input element, the second sun gear becomes the second control output element as the second gear, and the second control planetary gear mechanism is constituted,

9. The torque vector distribution device of claim 5,

the differential mechanism includes:

the first, second, and third planet gears;

a first ring gear of an internal gear, a second ring gear of an internal gear, and a third ring gear of an internal gear, which are coaxially arranged, the first ring gear being engaged with the first planetary gear, the second ring gear being engaged with the second planetary gear, the third ring gear being engaged with the third planetary gear; and

the wheel frame is arranged on the upper portion of the frame,

the first ring gear and the second and third ring gears are rotatable relative to each other,

the third ring gear becomes the power input element, the first ring gear becomes the first power output element, the carrier becomes the first differential reaction force element, and the first power planetary gear mechanism is constituted,

The third ring gear becomes the power input element, the second ring gear becomes the second power output element, and the carrier becomes the second differential reaction force element, thereby constituting the second power planetary gear mechanism,

the reversing mechanism includes:

the first, second, and third planet gears;

the first gear ring, the second gear ring, and the third gear ring; and

the wheel frame is arranged on the upper portion of the frame,

the carrier becomes the control input element, the first ring gear becomes the first control output element as the first gear, and the first control planetary gear mechanism is constituted,

the carrier becomes the control input element, the second ring gear becomes the second control output element as the second gear, and the second control planetary gear mechanism is constituted,

the number of teeth of the first gear ring is equal to that of the second gear ring and that of the third gear ring,

10. The torque vector distribution device of claim 5,

the differential mechanism includes:

the first, second, and third planet gears;

the wheel frame is arranged on the upper portion of the frame,

the first and second sun gears are rotatable relative to each other,

the reversing mechanism includes:

The first, second, and third planet gears;

the first sun gear, the second sun gear, and the third sun gear; and

the wheel frame is arranged on the upper portion of the frame,

the number of teeth of the first planetary gear is greater than that of the third planetary gear, and the number of teeth of the second planetary gear is less than that of the third planetary gear,

the torque vector distribution device further includes a reduction planetary gear mechanism that amplifies the control torque between the actuator and the carrier and transmits the amplified torque to the carrier.

11. The torque vector distribution device of claim 5,

The differential mechanism includes:

the first, second, and third planet gears;

the wheel frame is arranged on the upper portion of the frame,

the first and second sun gears are rotatable relative to each other,

the reversing mechanism includes:

the first, second, and third planet gears;

The first sun gear, the second sun gear, and the third sun gear; and

the wheel frame is arranged on the upper portion of the frame,

the torque vector distribution device further includes a reduction planetary gear mechanism that amplifies the control torque between the actuator and the carrier and transmits the amplified torque to the carrier,

the reduction planetary gear mechanism is composed of a fourth sun gear, a ring gear and the wheel carrier,

the fourth sun gear serves as the control input element, and the first sun gear serves as the first gear and serves as the first control output element, thereby compositely constituting the first control planetary gear mechanism,

the fourth sun gear serves as the control input element, and the second sun gear serves as the second gear and serves as the second control output element, thereby compositely constituting the second control planetary gear mechanism,

12. The torque vector distribution device of claim 11,

the reduction planetary gear mechanism has a fourth planetary gear simultaneously meshing with the fourth sun gear and the ring gear,

the fourth planetary gear is disposed coaxially with the first planetary gear, the second planetary gear, and the third planetary gear and is rotatable relative to the first planetary gear, the second planetary gear, and the third planetary gear,

the carrier holds the fourth planetary gear, the first planetary gear, the second planetary gear, and the third planetary gear together so as to be rotatable and revolvable, respectively.

13. The torque vector distribution device of claim 6,

the differential mechanism includes:

the first, second, third, and fourth planet gears;

a first ring gear of an internal gear, a second ring gear of an internal gear, a third ring gear of an internal gear, and a fourth ring gear of an internal gear, which are coaxially arranged, the first ring gear being engaged with the first planetary gear, the second ring gear being engaged with the second planetary gear, the third ring gear being engaged with the third planetary gear, the fourth ring gear being engaged with the fourth planetary gear; and

The wheel frame is arranged on the upper portion of the frame,

the third ring gear rotates integrally with the fourth ring gear,

the first and second ring gears and the third and fourth ring gears are rotatable relative to each other,

the fourth ring gear becomes the power input element, the second ring gear becomes the second power output element, and the carrier becomes the second differential reaction force element, thereby constituting the second power planetary gear mechanism,

the reversing mechanism includes:

the first, second, third, and fourth planet gears;

the first gear ring, the second gear ring, the third gear ring, and the fourth gear ring; and

the wheel frame is arranged on the upper portion of the frame,

the number of teeth of the first planetary gear is equal to that of the second planetary gear, the number of teeth of the third planetary gear is equal to that of the fourth planetary gear,

the number of teeth of the first ring gear is equal to the number of teeth of the second ring gear,

the number of teeth of the third ring gear is less than the number of teeth of the first ring gear and the number of teeth of the second ring gear, and the number of teeth of the fourth ring gear is more than the number of teeth of the first ring gear and the number of teeth of the second ring gear.

14. The torque vector distribution device according to claim 1 or 2,

with regard to the differential mechanism, it is preferable that,

the input member is coupled to the power input element,

the first power output element is coupled to the first drive shaft,

the second power output element is coupled to the second drive shaft,

the first differential reaction force element and the second differential reaction force element are linked to the actuator via the reverse mechanism,

with regard to the reverse-rotation mechanism, it is preferable that,

The actuator is coupled to the control input element,

the first gear forms the control input element or the first control output element,

the second gear forms the control input element or the second control output element,

the reverse mechanism amplifies and transmits the control torque input to the control input element to the first differential reaction element and the second differential reaction element.

15. The torque vector distribution device of claim 14,

with regard to the reverse-rotation mechanism, it is preferable that,

the first control planetary gear mechanism and the second control planetary gear mechanism form a reduction gear mechanism that amplifies the control torque,

the reverse mechanism transmits the control torque amplified by the first control planetary gear mechanism to the first differential reaction element, and transmits the control torque amplified by the second control planetary gear mechanism to the second differential reaction element.

16. The torque vector distribution device of claim 14,

the drive device is provided with a first output torque reduction mechanism and a second output torque reduction mechanism which are coaxially arranged to face each other in the left-right direction, wherein the first output torque reduction mechanism amplifies the torque transmitted to the first drive shaft, the second output torque reduction mechanism amplifies the torque transmitted to the second drive shaft,

The first power output element and the first drive shaft are coupled via the first output torque reduction mechanism,

the second power output element and the second drive shaft are coupled via the second output torque reduction mechanism,

the reversing mechanism is disposed between the first output torque reduction mechanism and the second output torque reduction mechanism in the rotation axis direction.

17. The torque vector distribution device of claim 14,

the reversing mechanism includes:

a first planetary gear, a second planetary gear, a third planetary gear and a fourth planetary gear which are coaxially arranged;

a first sun gear, a second sun gear, a third sun gear, and a fourth sun gear arranged on a same axis, the first sun gear being in mesh with the first planetary gear, the second sun gear being in mesh with the second planetary gear, the third sun gear being in mesh with the third planetary gear, the fourth sun gear being in mesh with the fourth planetary gear; and

the third sun gear is coupled to the fourth sun gear,

the first and second sun gears and the third and fourth sun gears are rotatable relative to each other,

the first sun gear is coupled to the first differential reaction element,

the second sun gear is coupled to the second differential reaction element,

the number of teeth of the first sun gear is equal to that of the second sun gear, the number of teeth of the third sun gear is equal to that of the fourth sun gear,

The number of teeth of the third planetary gear is equal to the number of teeth of the fourth planetary gear,

the number of teeth of the first planetary gear is more than the number of teeth of the third planetary gear and the number of teeth of the fourth planetary gear, and the number of teeth of the second planetary gear is less than the number of teeth of the third planetary gear and the number of teeth of the fourth planetary gear.

18. The torque vector distribution device of claim 14,

the reversing mechanism includes:

a first planetary gear, a second planetary gear and a third planetary gear which are coaxially arranged;

the first planetary gear and the second planetary gear and the third planetary gear each rotate integrally in a rotation direction,

the first and second sun gears are rotatable relative to each other,

The first sun gear is coupled to the first differential reaction element,

the second sun gear is coupled to the second differential reaction element,

the number of teeth of the first planetary gear is less than that of the third planetary gear, and the number of teeth of the second planetary gear is more than that of the third planetary gear.

19. The torque vector distribution device of claim 14,

the reversing mechanism includes:

a first sun gear, a second sun gear, a third sun gear, and a fourth sun gear arranged on a same axis, the first sun gear being in mesh with the first planetary gear, the second sun gear being in mesh with the second planetary gear, the third sun gear being in mesh with the third planetary gear, the fourth sun gear being in mesh with the fourth planetary gear;

a first carrier that holds the first planetary gears so as to be rotatable and revolvable, a second carrier that holds the second planetary gears so as to be rotatable and revolvable, and a third carrier that holds the third planetary gears and the fourth planetary gears so as to be rotatable and revolvable, which are coaxially arranged,

the first and second planet gears and the third and fourth planet gears are rotatable relative to each other,

the first sun gear rotates integrally with the third sun gear,

the second sun gear rotates integrally with the fourth sun gear,

the first and third sun gears and the second and fourth sun gears are rotatable relative to each other,

The first ring gear and the second ring gear and the third ring gear and the fourth ring gear each rotate integrally,

the first wheel frame, the second wheel frame and the third wheel frame can rotate relative to each other,

the first wheel carrier is coupled to the first differential reaction force element,

the second wheel carrier is coupled to the second differential reaction force element,

the first ring gear serves as the first gear to serve as the control input element, and the first carrier serves as the first control output element, thereby constituting the first control planetary gear mechanism,

the second ring gear serves as the second gear and serves as the control input element, and the second carrier serves as the second control output element, thereby constituting the second control planetary gear mechanism,

the number of teeth of the third sun gear is equal to the number of teeth of the fourth sun gear,

the number of teeth of the first sun gear is less than the number of teeth of the third sun gear and the number of teeth of the fourth sun gear, and the number of teeth of the second sun gear is more than the number of teeth of the third sun gear and the number of teeth of the fourth sun gear,

The number of teeth of the third ring gear is equal to the number of teeth of the fourth ring gear,

the number of teeth of the first ring gear is more than the number of teeth of the third ring gear and the number of teeth of the fourth ring gear, and the number of teeth of the second ring gear is less than the number of teeth of the third ring gear and the number of teeth of the fourth ring gear.

20. The torque vector distribution device of claim 14,

the reversing mechanism includes:

a first carrier, a second carrier, and a third carrier, which are coaxially arranged, the first carrier holding the first planetary gear so as to be rotatable and revolvable, the second carrier holding the second planetary gear so as to be rotatable and revolvable, the third carrier holding the third planetary gear so as to be rotatable and revolvable,

The first sun gear and the second sun gear and the third sun gear are integrally rotated,

the first ring gear and the second ring gear and the third ring gear each rotate integrally,

the number of teeth of the first planetary gear, the number of teeth of the second planetary gear and the number of teeth of the third planetary gear are all equal,

the number of teeth of the first sun gear is less than that of the third sun gear, and the number of teeth of the second sun gear is more than that of the third sun gear,

The number of teeth of the first ring gear is greater than that of the third ring gear, and the number of teeth of the second ring gear is less than that of the third ring gear.

21. The torque vector distribution device of claim 14,

the reversing mechanism includes:

an internal gear ring gear meshed with the second planetary gear; and

a first carrier and a second carrier that are coaxially arranged, the first carrier holding the first planetary gear and the third planetary gear so as to be rotatable and revolvable, the second carrier holding the second planetary gear so as to be rotatable and revolvable,

the first and third planet gears and the second planet gear are rotatable relative to each other,

The first and second sun gears are rotatable relative to each other,

the first wheel carrier and the second wheel carrier are rotatable relative to each other,

the first wheel carrier is connected with the second sun wheel,

the third sun gear and the ring gear are both fixed so as not to be rotatable,

the first sun gear is coupled to the first differential reaction element,

the first carrier serves as the control input element, and the first sun gear serves as the first gear and serves as the first control output element, thereby constituting the first control planetary gear mechanism,

the second sun gear serves as the second gear and serves as the control input element, and the second carrier serves as the second control output element, thereby constituting the second control planetary gear mechanism,

the gear ratio of the gear transmission path in which the control torque is transmitted to the first differential reaction element via the first carrier, the first planetary gears, and the first sun gear and the gear ratio of the gear transmission path in which the control torque is transmitted to the second differential reaction element via the second sun gear, the second planetary gears, and the second carrier are different from each other.

22. The torque vector distribution device according to any one of claims 17 to 21,

the input member has a hollow power torque output shaft for transmitting the power torque to the differential mechanism side,

the actuator has a hollow control torque output shaft for transmitting the control torque to the reverse mechanism side,

the reversing mechanism is disposed in a hollow portion of the power torque output shaft and a hollow portion of the control torque output shaft.

23. The torque vector distribution device of claim 15,

the actuator has a first rotating shaft and a second rotating shaft which are coaxially arranged to face each other in the left-right direction, the first rotating shaft protrudes toward the first drive shaft and outputs the control torque, the second rotating shaft protrudes toward the second drive shaft and outputs the control torque,

with regard to the reverse-rotation mechanism, it is preferable that,

the first control planetary gear mechanism and the second control planetary gear mechanism are disposed apart from each other on the left and right of the actuator in the rotation axis direction,

the first control planetary gear mechanism has a first input shaft to which the control torque is input and a first output shaft that transmits the control torque to the first drive shaft side,

The second control planetary gear mechanism has a second input shaft to which the control torque is input and a second output shaft that transmits the control torque to the second drive shaft side,

the first rotation shaft is coupled to the first input shaft,

the second rotation shaft is coupled to the second input shaft,

the first output shaft is coupled to the first differential reaction element,

the second output shaft is coupled to the second differential reaction element,

the gear ratio of the gear transmission path through which the control torque is transmitted to the first differential reaction element via the first rotation shaft, the first input shaft, and the first output shaft, and the gear ratio of the gear transmission path through which the control torque is transmitted to the second differential reaction element via the second rotation shaft, the second input shaft, and the second output shaft are different from each other.

24. The torque vector distribution device according to any one of claims 1 to 23,

the actuator is an electric motor that outputs, as the control torque, drive torque for driving the first differential reaction element and the second differential reaction element, or a brake mechanism that outputs, as the control torque, brake torque for braking the first differential reaction element and the second differential reaction element.

25. The torque vector distribution device according to any one of claims 1 to 24,

the power source is at least one of an electric motor that outputs, as the motive torque, a drive torque for driving the first drive shaft and the second drive shaft, and a brake mechanism that outputs, as the motive torque, a brake torque for braking the first drive shaft and the second drive shaft.